Heat Exchangers and Headers Therefor

ABSTRACT

In a first aspect of the present invention, a header for a heat exchanger is disclosed that has an inflow side, an outflow side, a bypass port therebetween, and a pressure-sensitive flapper valve proximal the bypass port. As pressure increases at the inflow side of the header, the flapper valve opens proportionally, and, as pressure decreases at the inflow side, the flapper valve closes proportionally. In a second aspect of the present invention, a tube-in-tube heat exchanger is disclosed that includes a helical tube-in-tube assembly adapted for flow therethrough of a plurality of fluids for heat transfer therebetween. In a third aspect of the present invention, a heat system is provided to include an embodiment of the header and an embodiment of the tube-in-tube heat exchanger, so as to provide a bypass of the tube-in-tube heat exchanger under a pressure condition.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is a continuation-in-part of U.S. patent application Ser. No. 11/698,792, filed Jan. 26, 2007, and is also a continuation-in-part of U.S. patent application Ser. No. 11/789,870, filed Apr. 26, 2007, the contents of both of which are incorporated herein by reference for all purposes.

FIELD OF THE INVENTION

In a first aspect, the present invention relates generally to a header for use with a heat exchanger and a fluid circulation line of a recreational body of water. In particular, exemplary embodiments of the present invention relate to a header that has means for bypassing the heat exchanger and/or means for initiating activation thereof. In a second aspect, the present invention relates generally to a tube-in-tube heat exchanger and methods of use thereof. In particular, exemplary embodiments of the invention relate to a tube-in-tube heat exchanger for use along a fluid circulation path of a recreational body of water. In a third aspect, the present invention relates generally to a heat system having a tube-in-tube heat exchanger and a header therefor.

BACKGROUND OF THE INVENTION

It is known in the art to utilize a header as an interface between a heat exchanger and a fluid circulation line of a recreational body of water, such as a swimming pool, spa, etc. The header typically has an inflow side that includes (1) a circulation line inlet that is downstream of the send of a fluid circulation line from the swimming pool, and (2) an exchanger line outlet that is upstream of the heat exchanger. Similarly, the header typically also has an outflow side that includes (1) an exchanger line inlet that is downstream of the heat exchanger, (2) and a circulation line outlet that is upstream of the return of the fluid circulation line.

Although any suitable nature and number of components can be installed along the fluid circulation path, e.g., pumps, filters, etc., it is desirable for the water flow rate through the heat exchanger to be optimized in a desired range. Otherwise, for example, a slower water flow rate through the heat exchanger can cause the heat exchanger to overheat, while a faster water flow rate through the heat exchanger can enhance corrosion and/or erosion.

The water flow rate through the heat exchanger is related to the pressure at the inflow side of the header, and, notwithstanding the desire to optimize water flow rate, it is not uncommon for higher pressures to build-up at the inflow side of the header of the prior art, thereby increasing the water flow rate through the heat exchanger. Such is the case, for example, because the exchanger line outlet of the header typically has a diameter greater than that of the pipes of the heat exchanger. Other potential causes for a high-pressure condition at the inflow side of the header can include, for example, a larger pump installed on the fluid circulation line, etc. What is needed in the art is a header for a heat exchanger that overcomes the disadvantages and shortcomings of the prior art.

Also, tube-in-tube assemblies for use in a heat exchanger are known in the art. An inner tube can be provided for the flow of refrigerant and an outer tube enclosing the inner tube can be provided for the flow therebetween of water. For example, United States Patent Publication No. 2003/0209345 discloses a tube-in-tube heat exchanger having a titanium tube for refrigerant surrounded by an outer spa hose, where the heat exchanger is helical for placement around a compressor. As another example, U.S. Pat. No. 5,802,864 discloses a refrigerant-to-water heat exchanger having a refrigerant conduit disposed within a water conduit, where a compressor is positioned within the exchanger. Among other advantages, a tube-in-tube design increases the surface area for which heat is exchanged between the refrigerant and the water. However, it is contemplated that heat exchangers experience inefficiencies by virtue of the outer water conduit being adjacent to the atmosphere. What is needed in the art is a heat exchanger that overcomes the disadvantages and shortcomings of the prior art.

SUMMARY OF THE INVENTION

The present invention includes at least three aspects and, without limiting the scope of any invention, the following is noted for the purposes of clarity of the present disclosure: (1) the first aspect of the present invention relates at least to a header for a heat exchanger; (2) the second aspect of the present invention relates at least to a tube-in-tube heat exchanger; and (3) the third aspect relates to a heat system having a tube-in-tube heat exchanger and a header therefor, wherein the tube-in-tube heat exchanger provides a primary passage for water flow and the header provides a bypass thereof. As used herein, the term “heat system” refers to a system that increases (makes hotter) and/or decreases (makes cooler) an amount of heat.

In the first aspect, the present invention overcomes the disadvantages and shortcomings of the prior art discussed above by providing a header having improved means for bypassing a heat exchanger and/or improved means for initiating activation thereof. In an exemplary embodiment of the present invention, the header includes an inflow side, an outflow side, a bypass port therebetween, and a pressure-sensitive flapper valve proximal the bypass port. As pressure increases at the inflow side of the header, the flapper valve opens, and, as the pressure decreases at the inflow side of the header, the flapper valve closes. In some exemplary embodiments of the present invention, the header has a service cartridge assembly that includes a frame and a flapper valve removably secured with respect to the frame, such that the service cartridge can be easily inserted into and/or removed from the header to facilitate easy repair and/or replacement of the flapper valve.

Continuing with discussion of the first aspect of the present invention, in some exemplary embodiments of the present invention, the header is provided with means for sensing a desired pressure differential across the heat exchanger and initiating heat exchanger activation in response to same. For example, a first pressure sensor is provided in fluid communication with the outflow side of the header to sense a first pressure thereof and a second pressure sensor is provided in fluid communication with the inflow side of the header to sense a second pressure thereof. A water flow rate is derived from the differential pressure between the outflow pressure and inflow pressure, and electro-mechanical and/or electronic means can be utilized to compare the water flow rate against a lower limit associated with the heat exchanger. Initiation of heat exchanger activation occurs when the measured flow rate has risen to meet and/or exceed the lower limit.

Additional features, functions and benefits of the disclosed header and header-related systems will be apparent from the detailed description which follows, particularly when read in conjunction with the accompanying figures corresponding thereto.

In the second aspect, the present invention overcomes the disadvantages and shortcomings of the prior art discussed above by providing a heat exchanger that includes a tank defining a chamber therein for receiving a helical tube-in-tube assembly and/or an external cavity for receiving a compressor, such a heat exchanger, for the purposes of clarity, referenced herein as a “tube-in-tube heat exchanger.” In the exemplary embodiment, the helical tube-in-tube assembly includes a water hose and a refrigerant tube at least partially extending through the water hose, where the refrigerant tube and the water hose define a primary water passage therebetween. Refrigerant flows through the refrigerant hose and water flows through the primary water passage for the exchange of heat with the refrigerant. It is contemplated that the helical tube-in-tube assembly can optionally be provided with centering means for centering the refrigerant tube within the water hose. In the exemplary embodiment, the tube-in-tube heat exchanger includes a diverter positioned within the chamber to direct a primary inflow of water into the primary water passage. In the second aspect, the diverter forms a loose seal with the tank to allow a leakage flow of water into the chamber external to the diverter, the tank defines a convergence area where the primary inflow of water and the leakage flow of water converge for flow out of the tank, and heat escaping from water flowing through the primary water passage is transferred to the leakage flow (and/or vice versa, as the case may be). In the second aspect, it is contemplated that the tube-in-tube heat exchanger can be provided with the substantially-enclosed diverter described below in connection with the third aspect of the present invention.

Continuing with discussion of the second aspect, in an exemplary embodiment of the present invention, the tube-in-tube heat exchanger includes at least one wall, such as a cylindrical wall, for defining the external cavity through the tank. The compressor can be positioned within the external cavity so as to be in fluid communication with the helical tube-in-tube assembly. A base and a cover can be provided to cooperate with the inner wall to at least partially enclose the compressor, thereby inhibiting the escape of sound from the external cavity. In the exemplary embodiment of the present invention, the tube-in-tube heat exchanger is provided with a seal assembly that is releasably secured to the tank so as to permit refrigerant flow between the refrigerant tube and a tube external of the tank, while inhibiting water flow out of the tank at the seal assembly. The external tube can be in fluid communication with the compressor (and/or other components suitable for the heat cycle). The seal assembly preferably includes a compression nut having an annular wall opposite the tank and an internally-threaded wall extending from the annular wall toward the tank and in engagement with external threads thereof. The seal assembly further includes (1) a cap positioned within the compression nut that abuts against the annular wall, (2) a piston positioned adjacent the tank, and (3) a grommet positioned between the cap and the piston. The compression nut, the cap, the grommet, and the piston define a continuous cylindrical opening through which the refrigerant tube extends. The grommet is compressed between the piston and the cap, thereby being deformed radially outward to form a seal with the refrigerant tube.

Continuing with further discussion of the second aspect, the tube-in-tube heat exchanger includes a plurality of legs, such as a first leg having a first elevation and a second leg having a second elevation greater than the first elevation. The legs are releasably securable to the tank. The tank includes a first post and a second post, and the first leg has a first depression adapted to securingly receive the first post, while the second leg has a second depression adapted to securingly receive the second post. In this regard, the second depression is shaped to inhibit insertion of the first post therein and the first depression is shaped to inhibit insertion of the second post therein. Additional features, functions and benefits of the disclosed tube-in-tube heat exchanger and related systems will be apparent from the detailed description which follows, particularly when read in conjunction with the accompanying figures corresponding thereto.

Additional features, functions and benefits of the disclosed tube-in-tube heat exchanger and related systems will be apparent from the detailed description which follows, particularly when read in conjunction with the accompanying figures.

In the third aspect of the invention, a heat system is provided with a tube-in-tube heat exchanger and a header, wherein each is configured for combination with the other. For example, the tube-in-tube heat exchanger can be provided with a substantially enclosed diverter for directing a flow of water through a primary water passage of the tube-in-tube heat exchanger and inhibiting leakage from the diverter. Continuing with the example, the header can be provided so as to allow flow to bypass the primary water passage of the tube-in-tube heat exchanger when there is a high-pressure condition and/or a pressure drop across the tube-in-tube heat exchanger.

As another example of the third aspect of the present invention, a heat system is provided for allowing and inhibiting temperature alteration of water from a fluid circulation line in accordance with a pressure of the water. The heat system can be provided with a heat exchanger and a header therefore. The heat exchanger can include a helical tube-in-tube assembly adapted for flow therethrough of water and another fluid for heat transfer therebetween, and the tube-in-tube assembly has defined therein a primary water passage with a first end and a second end. The heat exchanger can further include a tank with an annular chamber in which said helical tube-in-tube assembly is positioned, where the tank defines an external cavity extending axially therethrough. The header can be provided with an inflow side in fluid communication with the first end, an outflow side in fluid communication with the second end, a bypass therebetween, and a valve, such as a flapper valve. The valve, when oriented in a closed position, inhibits fluid flow from the inflow side to the outflow side through the bypass, and, when oriented in an at least partially open position, permits fluid flow from the inflow side to the outflow side through the bypass.

Additional features, functions and benefits of the disclosed heat system will be apparent from the detailed description which follows, particularly when read in conjunction with the accompanying figures.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more complete understanding of the present invention, reference is made to the following detailed description of exemplary embodiments considered in conjunction with the accompanying drawings, in which:

FIG. 1 is a plan view showing a header constructed in accordance with an exemplary embodiment of the present invention, the header being shown in combination with a fluid circulation line of a swimming pool and a heat exchanger having an electrical control system;

FIG. 2 is an exploded perspective view of the header of FIG. 1, the header being shown to include a manifold, a service cartridge assembly and lock ring therefor, a plurality of circulation line adapter assemblies, a plurality of exchanger line adapter assemblies, and a plurality of bolts;

FIG. 3 is a front perspective view showing the manifold of FIG. 2;

FIG. 4 is a rear perspective view showing the manifold of FIG. 2;

FIG. 5 is a left elevational view showing the header of FIG. 2 with the service cartridge and lock ring therefor having been removed;

FIG. 6 is a cross-sectional view showing the manifold, the service cartridge assembly, and the lock ring therefor of FIG. 2, the cross-section having been taken along section line 6-6 of FIG. 2;

FIG. 7 is a top view showing a base of one of the exchanger line adapter assemblies of FIG. 2;

FIG. 8 is a bottom view showing the base of FIG. 7;

FIG. 9 is a first perspective view showing the service cartridge assembly of FIG. 2, the service cartridge assembly being shown to include a handle, a frame, and a flapper valve;

FIG. 10 is a second perspective view showing the service cartridge assembly of FIGS. 2 and 9;

FIG. 11 is a left side elevational view showing the service cartridge assembly of FIGS. 2, 9, and 10;

FIG. 12 is a right side elevational view showing the service cartridge assembly of FIGS. 2 and 9-11 with the flapper valve being shown;

FIG. 13 is a perspective view showing the flapper valve of FIGS. 9, 10, and 12, the flapper valve being shown to include a torsion spring, a shaft, and a plurality of flappers;

FIG. 14 is an exploded perspective view showing the torsion spring, the shaft, and the plurality of flappers of FIG. 13;

FIG. 15 is a front elevational view showing an exemplary flapper valve in a closed position;

FIG. 16 is a front elevational view showing an exemplary flapper valve in an open position;

FIG. 17 is a table showing valve displacement as a function of water flow rate for the header of FIG. 1;

FIG. 18 is a table showing pressure drop as a function of water flow rate for the header of FIG. 1, where said pressure drop was measured between a circulation line inlet of the header and a circulation line outlet of the header;

FIG. 19 is a table showing differential pressure as a function of water flow rate for the header of FIG. 1, where said differential pressure was measured between an exchanger line outlet of the header and an exchanger line inlet of the header;

FIG. 20 is a top plan view of a heating unit that includes a tube-in-tube heat exchanger constructed in accordance with an exemplary embodiment of the present invention, the heating unit being shown to include a cabinet with a cover thereof having been removed, the tube-in-tube heat exchanger positioned within the cabinet and forming an external cavity, and a compressor positioned within the external cavity;

FIG. 21 is a perspective view of the tube-in-tube heat exchanger of FIG. 20;

FIG. 22 is a perspective view of the tube-in-tube heat exchanger of FIGS. 20 and 21, the tube-in-tube heat exchanger being shown to include a tank having an upper tank portion, a lower tank portion and a plurality of seals therebetween, a tube-in-tube assembly that is positioned within the tank and that has a refrigerant tube positioned within a water hose, a plurality of seal assemblies each at an end of the refrigerant tube, a water inlet nipple and a diverter positioned adjacent a first end of the water hose, a water outlet nipple positioned adjacent a second end of the water hose, a temperature sensor in fluid communication with the water inlet nipple, a plurality of legs, and a plurality of extension tubes for connecting the refrigerant tube to the compressor of FIG. 20;

FIG. 23 is a cross-sectional view of the tube-in-tube heat exchanger of FIGS. 20-22, the cross-section having been taken along section line 23-23 of FIG. 21;

FIG. 24 is a front elevational view of the lower tank portion of FIG. 22;

FIG. 25 is a sectional view of the lower tank portion of FIG. 24, the section having been taken along section line 25-25 of FIG. 24;

FIG. 26 is a top plan view of the lower tank portion of FIG. 22;

FIG. 27 is a first sectional view of the lower tank portion of FIG. 22, the first section having been taken along section line 27-27 of FIG. 26;

FIG. 28 is a second sectional view of the lower tank portion of FIG. 22, the section having been taken along section line 28-28 of FIG. 26;

FIG. 29 is a bottom plan view of the lower tank portion of FIG. 22, the lower tank portion being shown to have a plurality of shaped posts formed integrally therewith;

FIG. 30 is a perspective view of the diverter of FIG. 22;

FIG. 31 is a front elevational view of the upper tank portion of FIG. 22;

FIG. 32 is a sectional view of the upper tank portion of FIG. 31, the section having been taken along section line 32-32 of FIG. 31;

FIG. 33 is a top plan view of the upper tank portion of FIG. 31;

FIG. 34 is a first sectional view of the upper tank portion of FIG. 31, the first section having been taken along section line 34-34 of FIG. 33;

FIG. 35 is a second sectional view of the upper tank portion of FIG. 31, the section having been taken along section line 35-35 of FIG. 33;

FIG. 36 is a front elevational view of the outlet nipple of FIG. 22;

FIG. 37 is a cross-sectional view of the outlet nipple of FIGS. 22 and 36, the cross-section having been taken along section line 37-37 of FIG. 22;

FIG. 38 is a front elevational view of the inlet nipple of FIG. 22;

FIG. 39 is a cross-sectional view of the inlet nipple of FIGS. 22 and 38, the cross-section having been taken along section line 39-39 of FIG. 22;

FIG. 40 is an enlarged view of an end of the refrigerant tube of FIG. 22;

FIG. 41 is an exploded front perspective view of one of the seal assemblies of FIG. 22, the seal assembly being shown to include an O-ring, a piston, a grommet, a cap, and a compression nut;

FIG. 42 is an exploded rear perspective view of the seal assembly of FIG. 41;

FIG. 43 is a cross-sectional view of the seal assembly of FIGS. 41 and 42, the cross-section having been taken along section line 43-43 of FIG. 42;

FIG. 44 is a cross-sectional view of the seal assembly of FIG. 43 in combination with outlet threads of the upper tank portion of FIG. 131, the grommet of the seal assembly being compressed between the piston and the cap by the compression nut;

FIG. 45 is an elevational view of a tall one and a short one of the legs of FIG. 22;

FIG. 46 is a perspective view of the tall leg and the short leg of FIG. 45;

FIG. 47 is an enlarged view of a first one of the plurality of shaped posts shown in FIG. 29;

FIG. 48 is an enlarged view of a second one of the plurality of shaped posts shown in FIG. 29;

FIG. 49 is perspective view of the tube-in-tube assembly of FIG. 22 with the water hose being shown to be transparent for illustrative purposes only, the tube-in-tube assembly including a plurality of hangers for centering the refrigerant tube within the water hose;

FIG. 50 is a cross-sectional view of the tube-in-tube assembly of FIG. 49, the cross-section having been taken along section line 50-50 of FIG. 49;

FIG. 51 is a perspective view of a heat system that includes an embodiment of a tube-in-tube heat exchanger having a substantially enclosed diverter and that further includes an embodiment of a header in fluid communication with the tube-in-tube heat exchanger;

FIG. 52 is a cross-sectional view showing the header of FIG. 51, the cross-section having been taken along section line 52-52 of FIG. 51;

FIG. 53 is a rear perspective view of the substantially enclosed diverter included in the tube-in-tube heat exchanger of FIG. 51;

FIG. 54 is a rear exploded perspective view of the substantially enclosed diverter of FIG. 53, the substantially enclosed diverter being shown to include a first diverter portion and a second diverter portion.

FIG. 55 is a rear perspective view of the first diverter portion of FIG. 54;

FIG. 56 is a front elevational view of the first diverter portion of FIG. 54;

FIG. 57 is a rear elevational view of the first diverter portion of FIG. 54;

FIG. 58 is a left side elevational view of the first diverter portion of FIG. 54;

FIG. 59 is a right side elevational view of the first diverter portion of FIG. 54;

FIG. 60 is a top plan view of the first diverter portion of FIG. 54;

FIG. 61 is a bottom plan view of the first diverter portion of FIG. 54;

FIG. 62 is a rear perspective view of the second diverter portion of FIG. 54;

FIG. 63 is a front elevational view of the second diverter portion of FIG. 54;

FIG. 64 is a rear elevational view of the second diverter portion of FIG. 54;

FIG. 65 is a left side elevational view of the second diverter portion of FIG. 54;

FIG. 66 is a right side elevational view of the second diverter portion of FIG. 54;

FIG. 67 is a top plan view of the second diverter portion of FIG. 54; and

FIG. 68 is a bottom plan view of the second diverter portion of FIG. 54.

DETAILED DESCRIPTION OF THE EXEMPLARY EMBODIMENTS

With principal reference to FIGS. 1-19, the first aspect of the present invention shall now be discussed with further detail.

Referring to FIG. 1, a header 1010 is shown constructed in accordance with an exemplary embodiment of the present invention. The header 1010 is in fluid communication with a fluid circulation line 1012 of a recreational body of water, such as a swimming pool, spa, etc. A pump (not shown) is typically provided along the fluid circulation line 1012 for pumping water therethrough, and filter(s) and/or strainer(s) (not shown) are generally provided along the fluid circulation line 1012 for filtering/straining water upstream from the header 1010.

The header 1010 is provided in fluid communication with a heat exchanger 1014, such as the sinusoidal fin-type heat exchanger disclosed in U.S. Pat. No. 6,321,833, the contents of which are hereby incorporated by reference in their entirety. However, any suitable heat exchanger can be provided. An electrical control system 1016 is provided for managing activation and/or deactivation of the heat exchanger 1014 in accordance with sensed conditions, e.g., pressure and/or temperature, within the header 1010. Exemplary control systems may include programmed circuit boards and/or other electronic/electrical system(s). Also, it is contemplated that the electrical control systems can be structurally integrated with the heat exchanger 1010 and/or structural separate therefrom.

To facilitate further discussion and consideration of the header 1010, exemplary water flow thereto and therefrom has been designated as follows: water flow from the fluid circulation line 1012 to an inflow side 1018 of the header 1010 has been designated as flow path F_(IN1), water flow from the inflow side 1018 to the heat exchanger 1014 has been designated as flow path F_(IN2); water flow from the heat exchanger 1014 to an outflow side 1020 of the header 1010 has been designated as flow path F_(OUT1); and water flow from the outflow side 1020 to the fluid circulation line 1012 has been designated as a flow path F_(OUT2). The header 1010 facilitates bypass of the heat exchanger 1014, e.g. under high pressure conditions, and, to facilitate further consideration and discussion of same below, an exemplary bypass flow has been designated in FIG. 1 as flow path F_(B).

Referring to FIG. 2, the header 1010 includes a manifold 1022, a plurality of circulation line adapter assemblies 1024 a, 1024 b, a plurality of exchanger line adapter assemblies 1026 a, 1026 b, and a service cartridge assembly 1028. Each of the manifold 1022, the circulation line adapter assemblies 1024 a, 1024 b, the exchanger line adapter assemblies 1026 a, 1026 b, and the service cartridge assembly 1028 shall be discussed below with further detail.

Referring to FIGS. 2-6, the manifold 1022 can be provided as an integrated one-piece structure, though, as discussed below in connection with the third aspect of the present invention, it is contemplated that a manifold can be formed of a plurality of components. As disclosed in U.S. Pat. No. 6,026,804, the contents of which are hereby incorporated by reference in their entirety, the manifold 1022 is preferably formed from plastic due to economy of materials and corrosion resistance.

At the inflow side 1018, the manifold 1022 includes a substantially cylindrical wall 1030 that extends about a central axis, referenced herein as an inflow axis A_(IN). A bypass opening 1032 is formed transversely in the substantially cylindrical wall 1030 in alignment with a midpoint of the inflow axis A_(IN). The bypass opening 1032 has a central axis, referenced herein as a bypass axis A_(B), which extends perpendicularly with respect to the inflow axis A_(IN). An inlet, referenced herein as a circulation line inlet 1034, is formed at an end of the substantially cylindrical wall 1030. The circulation line inlet 1034 defines therein a first inflow chamber 1036 and is provided with external threads 1038. An annular groove 1040 is formed within the circulation line inlet 1034 at a terminus thereof.

An outlet, referenced herein as an exchanger line outlet 1042, is formed at an end of the substantially cylindrical wall 1030 opposite the circulation line inlet 1034. The exchanger line outlet 1042 defines therein a second inflow chamber 1044 and is provided with an annular rim 1046 spaced from a terminus of the exchanger line outlet 1042 opposite the circulation line inlet 1034.

Referring to FIGS. 1, 3-4, and 6, a temperature sensor 1048 is preferably provided in fluid communication with the second inflow chamber 1044 and in electrical communication with the electrical control system 1016 of FIG. 1. The temperature sensor 1048 is configured to sense a temperature of the water in the flow path F_(IN2) and send a corresponding temperature measurement to the electrical control system 1016. Should the water temperature along flow path F_(IN2) be lower than desired, the electrical control system 1016 will activate the heat exchanger 1014.

Referring to FIGS. 2-6, the manifold 1022 preferably includes a substantially annular bypass port 1050 that extends from the substantially cylindrical wall 1030 about the bypass axis A_(B). The bypass port 1050 defines a chamber therein, which is referenced herein as a bypass chamber 1052, and which is in fluid communication with first and second inflow chambers 1036, 1044 via the bypass opening 1032. The bypass port 1050 has an inner radius, which is designated as radius R₁ in FIG. 6. It is preferable that the radius R₁ be substantially similar, e.g., about equal, to a radius of the cylindrical wall 1030 (not designated) to increase potential flow along path F_(B).

The bypass port 1050 preferably has a drain opening (not designated) formed therein that receives a drain plug 1054 for manual release of fluid from the bypass chamber 1052. Also, the bypass port 1050 preferably has an opening (not designated) formed therein for receiving a stop plug 1056. It is contemplated that a user of the header 1010 can replace the stop plug 1056 with a pressure relief valve for exhausting pressurized fluid from the bypass port 1050 that exceeds a set point of the pressure relief valve.

At the outflow side 1020, the manifold 1022 includes an annular housing 1058 that is aligned with the bypass axis A_(B). The annular housing 1058 extends axially from the bypass port 1050 and, as further discussed below, is partially concentric therewith. The annular housing 1058 defines a chamber therein, which is referenced herein as a receiving area 1060 and which is sized and shaped to have the service cartridge assembly 1028 inserted therein. The receiving area 1060 has an inner radius, which is designated as radius R₂ in FIG. 6, and which is greater than the inner radius R₁ of the bypass port 1050.

A service opening 1062 is defined by the annular housing 1058 at an end thereof opposite the bypass port 1050, and the annular housing 1058 is provided with external threads 1064 proximal the service opening 1062. The annular housing 1058 has formed therein a plurality of openings, referenced herein as outflow openings 1066 a, 1066 b, which are partially aligned along an outflow axis A_(OUT) perpendicular with respect to the bypass axis A_(B) and parallel with respect to the inflow axis A_(IN). Each one of the outflow openings 1066 a, 1066 b is preferably circumferentially-spaced from each other one of the outflow openings 1066 a, 1066 b by about one-hundred and eighty degrees (180°).

Referring to FIGS. 5 and 6, the annular housing 1058 is, as indicated above, partially concentric with the bypass port 1050. In this regard, the annular housing 1058 and the bypass port 1050 form an annular channel 1068 therebetween, and the annular housing 1058 includes a tapered section 1070 that extends from the bypass port 1050 to enclose that side of the annular channel 1068 opposite the receiving area 1060. Circumferentially-displaced ribs, which are referenced herein as manifold ribs 1072 a, 1072 b, are positioned within the annular channel 1068 and extend axially from the bypass port 1050 to the annular housing 1058 to assist in aligning the service cartridge assembly 1028 when same is inserted in the receiving area 1060. Each one of the manifold ribs 1072 a, 1072 b is preferably displaced by about one-hundred and eighty degrees (180°) from each other one of the plurality of manifold ribs 1072 a, 1072 b. Additional ribs can be provided in the annular channel 1068 to assist in aligning the service cartridge assembly 1028, such as that which is shown and designated as a positioning rib 1074 in FIG. 5. Each one of the ribs 1072 a, 1072 b, 1074 preferably extends axially along the annular housing 1058 into the receiving area 1060. The annular channel 1068 and the ribs 1072 a, 1072 b, 1074 are sized and shaped to mate with the service cartridge assembly 1028 and inhibit rotation thereof. As will be discussed below with further detail, the bypass chamber 1052 of the bypass port 1050 is in fluid communication with the receiving area 1060 of the annular housing 1058 under certain pressure conditions.

Referring to FIGS. 2-6, at the outflow side 1020, the manifold 1022 includes a circulation line outlet 1076 proximal the outflow opening 1066 a, wherein the circulation line outlet 1076 is shown to be defined by a substantially annular wall extending from the annular housing 1058. The circulation line outlet 1076 defines therein a first outflow chamber 1078 and is provided with external threads 1080. An annular groove 1082 is formed within the circulation line outlet 1076 at a terminus thereof.

A plurality of temperature sensors 1084 a, 1084 b are preferably provided in fluid communication with the first outflow chamber 1078 and in electrical communication with the electrical control system 1016 of FIG. 1 (electrical connection path not shown). The temperature sensor 1084 a, for example, is configured to sense a temperature of the water in the flow path F_(OUT2) and send a corresponding temperature measurement to the electrical control system 1016. Temperature sensor 1084 b is redundantly provided as a safety measure. Should the water temperature along flow path F_(OUT2) be sensed by temperature sensor 1084 a and/or temperature sensor 1084 b as being greater than desired, the electrical control system 1016 will deactivate the heat exchanger 1014 in response thereto.

The manifold 1022 further includes an exchanger line inlet 1086 defined by a substantially annular wall extending from the annular housing 1058 proximal the outflow opening 1066 b. The exchanger line inlet 1086 defines therein a second outflow chamber 1088 and is provided with an annular rim 1090 spaced from the terminus of the exchanger line inlet 1086 opposite the annular housing 1058. Each one of the exchanger line inlet 1086, the circulation line outlet 1076, the exchanger line outlet 1042, and the circulation line inlet 1034 preferably has a radius (not designated) substantially equal to that of each other one of the exchanger line inlet 1086, the circulation line outlet 1076, the exchanger line outlet 1042, and the circulation line inlet 1034 The exchanger line inlet 1086 is slightly offset from the outflow axis A_(OUT).

Referring to FIGS. 1 and 3, a port, referenced herein as an outflow pressure port 1092, extends from the exchanger line inlet 1086 to define a chamber, referenced herein as an outflow sensing chamber 1094, that is in fluid communication with the second outflow chamber 1088. A pressure sensor, referenced herein as an outflow pressure sensor 1096, extends into the outflow pressure port 1092 to measure the pressure P_(OUT) of the water along the flow path F_(OUT1). Similarly, on the inflow side 1018, a port, referenced herein as an inflow pressure port 1098, extends from the exchanger line outlet 1042 to define a chamber, referenced herein as an inflow sensing chamber 1100, that is in fluid communication with the second inflow chamber 1044. A pressure sensor, referenced herein as an inflow pressure sensor 1102, extends into the inflow pressure port 1098 to measure a pressure P_(IN) of the water along the flow path F_(IN2).

The outflow pressure sensor 1096 and the inflow pressure sensor 1102 are utilized to have the electrical control system 1016 activate and/or deactivate the heat exchanger 1014 in accordance with a pressure differential ΔP, e.g., (P_(IN)−P_(OUT)). This may be accomplished by any suitable electro-mechanical and/or electronic means known in the art.

For example, as shown in FIG. 1, it is contemplated that the outflow pressure sensor 1096 sends the pressure P_(OUT) to the electrical control system 1016 and that the inflow pressure sensor 1102 sends the pressure P_(IN) to the electrical control system 1016, wherein an electronic processor compares (differences) P_(IN) and P_(OUT) to obtain a pressure differential ΔP. In this regard, it is contemplated that the electronic processor retrieves a pressure set point P_(SP) from memory associated therewith, and compares same with the pressure differential to identify if the set point has been reached/exceeded. The measuring and comparison can be done repetitively over time and, in the event that a rising pressure differential ΔP meets and/or exceeds the pressure set point P_(SP), the electrical control system 1016 initiates activation of the heat exchanger. At least with respect to a heat exchanger 1014 of the first aspect of the invention, the set point can be between about 0.1 pounds per square inch (PSI) and about 5.0 (PSI), and can also be between about 0.2 PSI and about 1.5 PSI. Notwithstanding, it is contemplated that any suitable set point can be provided.

As another example, it is contemplated that each one of the pressure sensors 1096, 1102 are components of a mechanical pressure differential switch (not shown) attached to the pressure ports 1092, 1098 to directly measure a difference in pressure between the two ports 1092, 1098. It is contemplated that each one of the sensors 1096, 1102 can include a movable diaphragm (not shown) responsive to the pressures of the sensing chambers 1094, 1100, and that a tube (not shown) can be provided to house both diaphragms A shaft (not shown) is secured to both diaphragms, and the diaphragms displace proportionally to the pressure at the respective ports 1092, 1098. The shaft is spring-loaded in such a manner that it may be calibrated to define a set-point for measuring a particular range of differential pressures. The shaft is connected to an electrical switch, such that the switch contacts are normally open, and the contacts are configured to close if the shaft is displaced an adequate distance relative to the set point of the spring. If both pressures are the same (the condition in which there is no water flow through the heat exchanger), the connecting shaft is stationary, and the switch contacts remain open. If the pressure at the inflow port 1098 is higher than the pressure at the outflow port 1092 by a predetermined amount, such as about 0.2-0.8 PSI in the first aspect of the present invention, then the switch contacts close to initiate activation of the heat exchanger 1014. If the pressure at the inflow port 1098 is less than the pressure at the outflow port 1092, such as in a reversed piping scenario, then the switch contacts remain open.

Referring to FIGS. 2-5, the manifold 1022 shall now be further discussed. The manifold 1022 includes a plurality of outwardly extending finger sets 1104 aligned along a shared plane. Each one of the finger sets 1104 includes a first finger (not designated), a second finger (not designated), and a passage (not designated) extending therebetween for receiving one of a plurality of bolts 1106 to secure the header 1010 to the heat exchanger 1014. Each one of the bolts 1106 can be provided with spacers and/or washers.

The exemplary manifold 1022 includes eight finger sets 1104, wherein two finger sets 1104 extend perpendicularly from the inflow side 1018 proximal the exchanger line outlet 1042 in a first direction, two finger sets 1104 extend perpendicularly from the inflow side 1018 proximal the exchanger line outlet 1042 in a second direction opposite the first direction, two finger sets 1104 extend perpendicularly from the outflow side 1020 proximal the exchanger line inlet 1086 in the first direction, and two finger sets 1104 extend perpendicularly from the outflow side 1020 proximal the exchanger line inlet 1086 in the second direction.

Continuing with reference to FIG. 2, the circulation line adapter assemblies 1024 a, 1024 b of the header 1010 are releasably securable to the manifold 1022 at the circulation line outlet 1076 and the circulation line inlet 1034, respectively. The circulation line adapter assemblies 1024 a, 1024 b shall now be discussed with exemplary reference to the circulation line adapter assembly 1024 a. It shall be clear to one skilled in the art that the below discussion of the circulation line adapter 1024 a is equally applicable to the circulation line adapter 1024 b.

The circulation line adapter assembly 1024 a has a seal 1108 a, a circulation line fitting 1110 a, and a lock ring 1112 a. The seal 1108 a, which is preferably formed from an elastomeric material, is positioned within the annular groove 1082 and extends radially therefrom. The line fitting 1110 a, which is preferably formed from a plastic material, includes an annular wall 1114 a extending about the outflow axis A_(OUT). The line fitting 1110 a further includes a flange 1116 a that extends radially from an end of the annular wall 1114 a and that abuts the seal 1108 a. The inner radius (not designated) of the annular wall 1114 a is substantially equal to the inner radius (not designated) of the circulation line outlet 1076, though the outer radius (not designated) of the annular wall 1114 a is less than the outer radius (not designated) of the circulation line outlet 1076. In this regard, the lock ring 1112 a includes a radially extending section 1118 a and an internally-threaded section 1120 a depending therefrom, such that the annular wall 1114 a extends through the radially extending section 1118 a of the lock ring 1112 a, and such that the external threads 1080 of the circulation line outlet 1076 cooperate with the internally-threaded section 1120 a of the lock ring 1112 a to secure the line fitting 1098 a against the circulation line outlet 1076.

Similarly, the circulation line adapter assembly 1024 b includes a seal 1108 b, a circulation line fitting 1110 b, and a lock ring 1112 b. The seal 1108 b is positioned within the annular groove 1040 and extends radially therefrom. The line fitting 1110 b includes an annular wall 1114 b extending about the inflow axis A_(IN) and further includes a flange 1116 b abutting the seal 1108 b. The lock ring 1112 b includes a radially extending section 1118 b and an internally-threaded section 1120 b depending therefrom, such that the annular wall 1114 b extends through the radially extending section 1118 a of the lock ring 1112 b, and such that the external threads 1038 of the circulation line inlet 1034 cooperate with the internally-threaded section 1120 b of the lock ring 1112 b to secure the line fitting 1110 b against the circulation line inlet 1034.

Referring to FIGS. 2 and 7-8, the exchanger line adapter assemblies 1026 a, 1026 b of the header 1010 are releasably securable to the manifold 1022 at the exchanger line inlet 1086 and the exchanger line outlet 1042, respectively. As further discussed below, the exchanger line adapter assemblies 1026 a, 1026 b include O-rings 1122 a, 1122 b, respectively, and bases 1124 a, 1124 b, respectively.

The exchanger line adapter assemblies 1026 a, 1026 b shall now be discussed with exemplary reference to the exchanger line adapter assembly 1026 a. It shall be clear to one skilled in the art that the below discussion of the exchanger line adapter assembly 1026 a is equally applicable to the exchanger line adapter assembly 1026 b.

The O-ring 1122 a, which is preferably formed from an elastomeric material, such as rubber, extends circumferentially about the exchanger line inlet 1086. The base 1122 a, which is preferably formed from plastic, includes a tiered-section 1126 a having a first depression area 1128 a with a first diameter (not designated) and a second depression area 1130 a with a second diameter less than the first diameter (not designated). A surface, referenced herein as a seat 1132 a, extends across a terminus of the second depression area 1130 a opposite the first depression area 1128 a. A plurality of openings, referenced herein as exchanger ports 1134 a, are formed in the seat 1132 a and each one of a plurality of conduits 1136 a extend from one of the plurality of exchanger ports 1134 a.

The base 1124 a has a plurality of boreholes 1138 a formed therein for receiving bolts 1106 extending from the manifold 1022 to securingly retain the base 1124 a against the manifold 1022. When the base 1124 a is secured to the manifold 1022, the first depression area 1128 a receives the annular rim 1090 and the O-ring 1122 a, while the area extending therefrom to the terminus of the exchanger line inlet 1086 is received by the second depression area 1130 a and abuts the seat 1132 a.

Referring to FIGS. 2, 6, and 9-12, an exemplary service cartridge assembly 1028 of the header 1010 shall now be discussed with further detail. The service cartridge assembly 1028, which includes a frame 1140, a handle 1142, a plurality of O-rings 1144, and a flapper valve 1146, is positioned within the receiving area 1060 of the annular housing 1058. The service cartridge assembly 1028 defines therein a third outflow chamber 1148.

An internally-threaded lock ring 1150 cooperates with the external threads 1064 proximal the service opening 1062 to inhibit inadvertent removal of the service cartridge assembly 1028 therethrough. When the lock ring 1150 is disengaged from the external threads 1064 of the service opening 1062, the service cartridge assembly 1028 is removable for servicing and/or replacement of the service cartridge assembly 1028 and/or the components thereof, e.g., the flapper valve 1146, etc.

The frame 1142 of the service cartridge assembly 1028 includes a circular wall 1152 aligned along the bypass axis A_(B), and the handle 1142 extends from the circular wall 1152 in a direction opposite the receiving area 1060. The frame 1142 further includes a grooved annulus 1154 extending perpendicularly from the circular wall 1152 into the receiving area 1060. To effect a seal between the service cartridge assembly 1028 and the annular housing 1058, the outer radius of the grooved annulus 1154 is just less than the inner radius R₂ of the annular housing 1058, and each one of the plurality of O-rings 1144 are positioned within each one of the annular grooves (not designated) of the grooved annulus 1154.

A plurality of ribs, which are referenced herein as cartridge ribs 1156, are circumferentially displaced along a side of the grooved annulus 1154 opposite the handle 1142 and extend perpendicularly from the grooved annulus 1154. A generally cylindrical wall is provided with a slight tapering, which is referenced herein as a tapered wall 1158. The tapered wall 1158 is at least partially bound by the cartridge ribs 1156 and extends from the grooved annulus 1154 to an annular lip 1160 defining a third opening in the frame 1142, referenced has a valve opening (not designated). The tapered wall 1158 is tapered toward the grooved annulus, such that the tapered wall 1158 has a greater outer radius proximal the annular lip 1160 and a lesser outer radius proximal the grooved annulus 1154.

A first hole 1162 a is formed in the tapered wall 1158 proximal the outflow opening 1066 a in the manifold 1022, such that the third outflow chamber 1148 is in fluid communication with the first outflow chamber 1078 of the circulation line outlet 1076. Similarly, a second hole 1162 b is formed in the tapered wall 1158 proximal the outflow opening 1066 b in the manifold 1022, such that the third outflow chamber 1148 is in fluid communication with the second outflow chamber 1088 of the exchanger line inlet 1086.

The tapered wall 1158 has a plurality of rectangular channels 1164 a, 1164 b formed therein that extend from the annular lip 1160 to the first and second holes 1162 a, 1164 b, respectively. The rectangular channels 1164 a, 1164 b are preferably circumferentially-displaced about the tapered wall 1158 by about one hundred and eighty degrees (180°). As will be discussed with further detail below, the rectangular channels 1164 a, 1164 b assist in securing the flapper valve 1146 to the frame 1140.

Referring to FIGS. 5 and 12, a notched flange 1166 extends axially from an inner circumference of the annular lip 1160 and mates with the annular channel 1068 formed at the juncture of the housing 1058 and the bypass port 1050. More particularly, the notched flange 1166 includes a plurality of notches 1168 a, 1168 b that extend through the annular lip 1160 and that are sized and dimensioned to mate with the manifold ribs 1072 a, 1072 b to inhibit rotation of the service cartridge assembly 1028. The notches 1168 a, 1168 b are preferably circumferentially-displaced by about one hundred and eighty degrees (180°) to correspond with the manifold ribs 1072 a, 1072 b. The notched flange 1166 preferably further includes a positioning notch 1170 mating with the positioning rib 1074. The positioning notch 1170 and the positioning rib 1074 cooperate to ensure that the service cartridge assembly 1028 has been inserted into the receiving area 1060 in the desired spatial orientation.

Referring to FIG. 12, a shoulder 1172 a is formed in the tapered wall 1158 adjacent the notch 1168 a and proximal the annular lip 1160. Similarly, a shoulder 1172 b is formed in the tapered wall 1158 adjacent the notch 1168 b and proximal the annular lip 1160. Each one of the shoulders 1172 a, 1172 b is preferably circumferentially-displaced about the tapered wall 1158 from each other one of the shoulders 1172 a, 1172 b by about one hundred and eighty degrees (180°). Also, each one of the shoulders 1172 a, 1172 b is preferably circumferentially-displaced about the tapered wall 1158 from each one of the rectangular channels 1164 a, 1164 b adjacent thereto by about ninety degrees (90°). As will be discussed with further detail below, the shoulders 1172 a, 1172 b assist in securing the flapper valve 1146 to the frame 1140.

Referring to FIGS. 6, 9, 10, and 12-15, the flapper valve 1146 preferably includes a shaft 1174, a torsion spring 1176, and a plurality of hinged pieces, which are referenced herein as flappers 1178 a, 1178 b. The flappers 1178 a, 1178 b shall be discussed with exemplary reference to the flapper 1178 a. It shall be clear to one skilled in the art, however, that discussion below of the flapper 1178 a is equally applicable to the flapper 1178 b.

The flapper 1178 a, which can be formed from polypropylene, includes a semicircular portion 1180 and a plurality of hinges 1182 a, 1182 b extending from the semicircular portion 1180. Each one of the hinges has formed in a first side thereof a first U-shaped channel (not designated) and, in a second side opposite the first side, a second U-shaped channel (not designated) that is inverted with respect to the first U-shaped channel. The shaft 1174 extends through the hinges 1182 a, 1182 b and extends through a central space (not designated) of the torsion spring 1176.

Referring to FIGS. 5 and 12, the shaft has a first end 1184 a positioned within the shoulder 1172 a of the frame 1140 and a second end 1184 b positioned within the shoulder 1174 b of the frame 1140. The manifold ribs 1072, 1072 b of the housing 1058 extend into the notches 1168 a, 1168 b, which thereby secures the ends 1184 a, 1184 b in the shoulders 1174 a, 1174 b, respectively. The shaft is preferably formed from type-316 stainless steel. In this regard, the torsion spring 1176 is preferably formed from type-316 stainless steel spring wire.

Referring to FIGS. 6 and 12-14, the flapper 1178 a includes a first side 1186 facing the bypass chamber 1052, a second side 1188 facing the third outflow chamber 1148, a straight edge 1190 that is substantially parallel with respect to the shaft 1174, and a curved edge 1192 that is proximal the frame 1140. The flapper 1178 a further includes a curved extension 1194 extending from the first side 1186 at the straight edge 1190. The curved extension 1194 of the flapper 1178 a and the curved extension 1194 of the flapper 1178 b cooperate to receive the torsion spring 1176. When the flapper valve 1146 is in a closed position, the curved extensions 1194 abut one another at ends thereof to inhibit reverse rotation of the flappers 1178 a, 1178 b. Furthermore, referring to FIG. 12, the flapper 1178 a preferably includes a stop 1196 and a stop surface 1198 complementary thereto, such that, when the flapper valve 1146 is in the closed position, the stop 1196 of the flapper 1178 a abuts the stop surface 1198 of the flapper 1178 b and the stop 1196 of the flapper 1178 b abuts the stop surface 1198 of the flapper 1178 to inhibit reverse rotation of the flappers 1178 a, 1178 b.

Referring to FIGS. 6 and 9-14, the flapper 1178 a includes a protrusion 1200 extending from the second side 1188 that is aligned with an imaginary bisector thereof. As shown, the protrusion 1200 includes a beveled edge (not designated), such that the beveled edges of the flappers 1178 a, 1178 b make contact at a fully-open position of the flapper valve 1146. The protrusion 1200 begins proximal the straight edge 1190 and extends past the boundary of the curved edge 1192, such that an end of the protrusion 1200, referenced herein as the protrusion end 1202, is spaced apart from the semicircular portion 1180. In this regard, when the flapper valve 1146 is in the closed position, the protrusion end 1202 of the flapper 1178 a is positioned within the rectangular channel 1164 a of the frame 1140 and the protrusion end 1202 of the flapper 1178 a is positioned within the rectangular channel 1164 b. In this regard, in the closed position of the flapper valve 1146, the torsion spring 1176 has a rotational force applied to the flappers 1178 a, 1178 b, such that the protrusion end 1202 of each one of the flappers is secured within the corresponding one of the channels 1164 a, 1164 b.

Referring to FIGS. 1, 6, 12, 13, and 15, which show the flapper valve 1146 in a closed position, the flapper 1178 a is angularly displaced from the flapper 1178 b by about one-hundred and eighty degrees (180°), thereby obstructing fluid flow from the bypass chamber 1052 to the third outflow chamber 1148 along the flow path F_(B).

However, as shown in FIG. 16, when a high-pressure condition exists in the bypass chamber 1052, the flapper 1178 a is angularly displaced, thereby permitting fluid flow from the bypass chamber 1052 to flow to the third outflow chamber 1148 along the flow path F_(B). In the open positions, the flapper 1178 b is angularly displaced from the closed position by as much as an angle θ₁, which is preferably about fifty degrees (50°), and the flapper 1178 a is angularly displaced from the closed position by an angle θ₂, which is preferably also about fifty degrees (50°), for a preferred maximum displacement of two-hundred and eighty-degrees (280°). Thus, when the angular displacement between the flapper 1178 a and the flapper 1178 b is greater than one-hundred and eighty degrees (180°), water can flow from the bypass chamber 1052 to the third outflow chamber 1148 along the flow path F_(B).

The flapper valve 1146 is releasably securable to the frame 1140. For example, when the flapper valve 1146 is secured to the frame 1140 within the manifold 1022, the service cartridge assembly 1028 is removed therefrom by a user, who then rotates the flapper valve 1146 into an open position, such that the protuberance ends 1202 have moved out of the channels 1164 a, 1164 b, through the holes 1162 a, 1162 b, and into the third inflow chamber 1148. The flapper valve 1146 is then pulled in a direction opposite the circular wall 1152 through the valve opening defined by the annular lip 1160 of the frame 1140. Similarly, to install the flapper valve 1146, a user rotates the flapper valve 1146 into an open position, inserts the shaft ends 1184 a, 1184 b into the shoulders 1172 a, 1172 b and then releases the flapper valve 1146, allowing the protuberance ends 1202 to move in response to the force of the torsion spring 1176 into the channels 1164 a, 1164 b.

Referring to FIG. 17, the total angular displacement between the flappers 1178 a, 1178 b is a function of the water flow rate on flow paths F_(IN1) and/or F_(IN2). As water flow is increased, the flapper valve 1146 opens proportionally to allow more water to bypass those heat exchanger tubes proximal the exchanger line outlet 1042, keeping the water flow rate through the heat exchanger 1010 at the optimum flow rate.

Referring to FIGS. 18 and 19, exemplary embodiments of the header 1010 provide enhanced optimization of water flow rate through the heat exchanger 1014 and minimize the differential pressure, also known as “pressure drop”, across the heat exchanger 1014. By reducing the pressure drop associated with the heat exchanger 1014, the header 1010 enables a higher total water flow rate in a pool and/or spa system to be provided with a smaller circulation pump. Furthermore, as shown in FIG. 19 and with continuing discussion of the first aspect of the invention, the differential pressure appears to have minimal deviation when the “back pressure” (pressure in the bypass chamber 1052) varies from a low pressure, such as about two (2) PSI, to a medium pressure, such as about ten (10) PSI, and to a high pressure, such as about forty (40) PSI.

With principal reference to FIGS. 20-50, the second aspect of the present invention shall now be discussed with further detail.

Referring to FIG. 20, a top plan view of a heating unit 2010 is shown. The heating unit 2010 is in fluid communication with a fluid circulation line (not shown in FIG. 20) of a recreational body of water, such as a swimming pool, spa, etc. A pump (not shown) is typically provided along the fluid circulation line for pumping water therethrough, and filter(s) and/or strainer(s) (not shown) are provided along the fluid circulation line for filtering/straining water upstream from the heating unit 2010. The heating unit 2010 includes an enclosed cabinet 2012, which has a base plate 2014, a cylindrical cabinet side wall 2016, and a cover 2018 that is shown in FIG. 20 to have been removed to reveal a cabinet space (not designated) defined within the cabinet 2012. A tube-in-tube heat exchanger 2020 constructed in accordance with an exemplary embodiment of the present invention is shown to be positioned within the space of the cabinet 2012 and fastened to the base plate 2014 and, for the purposes of clarity of disclosure, is referenced herein as the tube-in-tube heat exchanger 2020.

Referring to FIGS. 20 and 21, the tube-in-tube heat exchanger 2020 includes a water outlet nipple 2022 and a water inlet nipple 2024 that each extend through the cabinet side wall 2016 to facilitate attachment thereof to the fluid circulation line without removal of the cover 2018 being required. The tube-in-tube heat exchanger 2020 defines an external cavity 2026 in which a compressor 2028 is shown to be positioned. A plurality of external tube extensions 2030 a, 2030 b can be provided between the tube-in-tube heat exchanger 2020 and the compressor 2028 for fluid communication therebetween of refrigerant. Additional components of the heating unit 2010 for use in the heat cycle can be in communication with the extensions 2030 a, 2030 b. As discussed with further detail below, the tube-in-tube heat exchanger 2020 is adapted to have water flow therethrough from the water inlet nipple 2024 to the water outlet nipple 2022, during which time heat is transferred, such as from the refrigerant to the water. Also discussed below, the position of the compressor 2028 within the external cavity 2026 reduces the amount of sound from the compressor 2028 that is perceptible by a user of the tube-in-tube heat exchanger 2020, e.g., the amplitude of compressor noise escaping the tube-in-tube heat exchanger 2020 is minimized.

Referring to FIGS. 21-23, the tube-in-tube heat exchanger 2020 includes a tank 2032 that defines an annular chamber 2034 extending about a central axis A_(T) and that further defines the external cavity 2026 along the central axis A_(T). The tank 2032 includes an upper tank portion 2036, a lower tank portion 2038 electromagnetically welded thereto, and a plurality of ribbon seals 2040 a, 2040 b positioned between the upper tank portion 2036 and the lower tank portion 2038. A plurality of legs 2042 a-c are provided for supporting the tank 2032. In those embodiments of the invention in which the tube-in-tube heat exchanger 2020 is provided with the heating unit 2010, the legs 2042 a-c can be used in combination with screws 2044 a-c for removably securing the tank 2032 to the base plate 2014 of the heating unit 2010.

The tube-in-tube heat exchanger 2020 includes a tube-in-tube assembly 2046 that has a spiral shape and that is positioned within the annular chamber 2034 of the tank 2032 to extend helically about the axis A_(T). The external cavity 2026 extends in an axial direction and through the tube-in-tube-assembly 2046. The tube-in-tube assembly 2046 includes a water hose 2048 and a refrigerant tube 2050 extending therethrough. The refrigerant tube 2050 is preferably formed from titanium and is adapted for having refrigerant flow therethrough. The water hose 2048 terminates at ends thereof that are referenced herein as water hose ends 2052 a, 2052 b. The refrigerant tube 2050 extends out past the water hose ends 2052 a, 2052 b and terminates outside the water hose 2048 at ends that are referenced herein as refrigerant tube ends 2054 a, 2054 b. Lock rings 2056 a, 2056 b secure the refrigerant tube ends 2054 a, 2054 b, respectively, to the external tube extensions 2030 a, 2030 b, respectively, for fluid communication of the refrigerant between the refrigerant tube 2050 and the compressor 2028.

A primary water passage 2058 is defined by an annular space formed between the water hose 2048 and the refrigerant tube 2050. The primary water passage 2058 is in fluid communication with the water outlet nipple 2022 and the water inlet nipple 2024, which are provided with O-rings referenced herein as ring seals 2060 a, 2060 b. The water inlet nipple 2024 and the water outlet nipple 2022 are adapted for fluid communication with the fluid circulation line of the recreational body of water, e.g., swimming pool, spa, etc., to receive water to be heated in the primary water passage 2058 by the refrigerant tube 2050 and to provide water that has been heated by the refrigerant tube 2050, respectively. The water inlet nipple 2024 is provided with a temperature sensor 2062, a mounting strap 2064 therefor, a drain plug 2066, and a drain plug seal 2068. Also, a water diverter 2070 is positioned within the annular chamber 2034 adjacent the water inlet nipple 2024. The water diverter 2070 is sized and shaped to direct principal water flow to the primary water passage 2058 (and, in the second aspect of the present invention, is loosely fitted against the tank 2032 to facilitate a secondary “leakage flow” of water outside of the primary water passage 2058 for upward flow through the annular chamber 2034). It is preferable that the direction of principal water flow through the primary water passage 2058 be counter to the direction of refrigerant flow through the refrigerant tube 2050. A plurality of seal assemblies 2072 a, 2072 b are provided for sealing the refrigerant tube ends 2054 a, 2054 b, such that water is inhibited from escaping the tank 2032 at the seal assemblies 2072 a, 2072 b. Each one of the seal assemblies 2072 a, 2072 b includes an O-ring 2074, a piston 2076, a grommet 2078, a cap 2080, and a compression nut 2082, which shall each be discussed in further detail below with principal reference to FIGS. 41-44.

Referring to FIGS. 24-29 and 31-35, the tank 2032 includes a lower tank portion 2038 and an upper tank portion 2036 electromagnetically welded therewith. As shall be further discussed below with further detail, both the lower tank portion 2038 and the upper tank portion 2036 include an inner wall portion (designated below as portions 2084, 2122) that cooperate to define an inner wall of the tank 2032 through which the external cavity 2026 extends. Also, both the lower tank portion 2038 and the upper tank portion 2036 include an outer wall portion (designated below as portions 2086, 2124) that cooperate to define an outer wall of the tank 2032.

Referring to FIGS. 24-29, the lower tank portion 2038 of the tank 2032 shall now be discussed with further detail. The lower tank portion 2038 includes at least one inner wall portion 2084 extending about the axis A_(T) to define a portion of the external cavity 2026 and at least one outer wall portion 2086 extending about the axis A_(T), such that the inner wall portion 2084 and the outer wall portion 2086 define therebetween a portion of the annular chamber 2034. The lower tank portion 2038 further includes a bottom wall 2088 extending from the inner wall portion 2084 to the outer wall portion 2086 to at least partially enclose the annular chamber 2034.

The inner wall portion 2084 of the lower tank portion 2038 terminates at an end opposite the bottom wall 2088 with a first annular finger set 2090 having a first pair of annular fingers that define a first annular space therebetween. Similarly, the outer wall portion 2086 of the lower tank portion 2038 terminates at an end opposite the bottom wall 2088 with a second annular finger set 2092 having a second pair of annular fingers that define a second annular space therebetween. The first and second annular finger sets 2090, 2092 mate with the upper tank portion 2036 to securingly align the lower tank portion 2038 thereto during electromagnetic welding of the tank portions 2036, 2038 to one another.

With principal reference to FIG. 27, the outer wall portion 2086 has a first elevation E₁ and the inner wall portion 2084 has a second elevation E₂ greater than the first elevation E₁. Also, an imaginary geometric plane aligned with the annular finger set 2092 has been designated in FIG. 27 as plane H_(O) for the purpose of showing that the distance between the plane H_(O) and the bottom wall 2088 is preferably multiform. For example, in the exemplary embodiment of the present invention, there is a first distance H₁ between the plane H_(O) and the bottom wall 2088 and a second distance H₂ between the plane H_(O) and the bottom wall 2088 that is greater than the first distance H₁. More particularly, the bottom wall 2088 is preferably inclined such that the distance from the finger set 2092 to the bottom wall 2088 increases between from the distance H₁ to the distance H₂.

Continuing with reference to FIGS. 24-29, the lower tank portion 2038 includes a drain opening 2094, an alignment tab 2096, and a plurality of shaped posts 2098 a-c. The drain opening 2094 extends from the outer wall portion 2086 of the lower tank portion 2038 and is preferably plugged with a removable drain plug (not shown). The alignment tab 2096 is positioned along the outer wall portion 2086 of the lower tank portion 2038 proximal the finger set 2092 for securingly aligning the upper tank portion 2036 with the lower tank portion 2038 during attachment of the upper tank portion 2036 thereto, such as by electromagnetic welding. The shaped posts 2098 a-c are provided for engaging the legs 2042 a-c and shall be discussed with further detail below in connection with the legs 2042 a-c.

The lower tank portion 2038 has formed therein a plurality of passages, including a water inlet passage 2100 and a refrigerant tube outlet 2102. Each of the water inlet passage 2100 and the refrigerant tube outlet 2102 extend from the outer wall portion 2086 proximal the bottom wall 2088. The refrigerant tube outlet 2102 has external threads 2104 for engagement with the seal assembly 2072 b. The water inlet passage 2100 preferably extends about ninety degrees with respect to the refrigerant tube outlet 2102. The water inlet passage 2100 has an annular groove 2106 formed at an end thereof for receiving the ring seal 2060 b and is further discussed below in connection with the water inlet nipple 2024.

Referring to FIGS. 22-23, 25, 28, and 30, the annular chamber 2034 includes an area proximal the water inlet passage 2100 that is referenced herein as a water diversion area 2108. In the second aspect of the present invention, the water diversion area 2108 is a space defined by the diverter 2070 of FIGS. 22, 23, and 30. As further discussed below, in the second aspect of the present invention, the diverter 2070 forms a loose seal with the outer wall portion 2086 to channel a principal flow of water from the water inlet passage 2100 into the primary water passage 2058 while allowing a desired amount of leakage flow of water into that area of the annular chamber 2034 outside the water diversion area 2108.

As shown in FIG. 30, in the second aspect of the invention, the diverter 2070 can be configured to sit atop the bottom wall 2088 of the lower tank portion 2038 within the annular chamber 2034. The diverter 2070 includes a first retaining wall 2110 having an opening 2112 formed therethrough. The water hose 2048, which is preferably corrugated, extends through the opening 2112, such that the water hose end 2052 a is securingly retained by the first retaining wall 2110. The refrigerant tube 2050 extends through the water diversion area 2108, and the diverter 2070 includes a second retaining wall 2114 defining an opening 2116 through which the refrigerant tube end 2054 b extends. In the second aspect of the present invention, the diverter 2070 further includes a plurality of walls 2118 a-c that extend between the first and second retaining walls 2110, 2114 and cooperate with the first and second retaining walls 2110, 2114 and the outer wall portion 2086 to at least partially enclose the diversion area 2108. In the second aspect of the present invention, the walls 2110, 2114, 2118 a, 2118 b, and 2118 c can form a loose seal with the bottom wall 2088 and/or the outer wall portion 2086, such that water flowing into the diversion area 2070 from the water inlet passage 2100 is principally channeled into the primary water passage 2058 at the water hose end 2052 a. At the same time, in the second aspect of the invention, the loose seal allows a secondary, leakage flow of water flow into that portion of the annular chamber 2034 outside of the diverter 2070, such that the annular chamber 2034 fills with water to the top of the upper tank portion 2036 of the tank 2032. As discussed further below, in the second aspect of the invention, it is contemplated that leakage flow from the diverter 2070 into the annular chamber 2034 generally can be utilized to bypass the primary water passage 2058 when the pressure and/or water flow rate is undesirably high. Also, the water outside the water hose 2048 in the annular chamber 2034 absorbs that heat escaping through the wall of the hose 2048 from that water in the primary water passage 2058. In the second aspect of the invention, the diverter 2070 includes a hook 2120 for securing the diverter 2070 at an eyehole (not shown) formed in the lower tank portion 2038 to inhibit the diverter 2070 from floating to the top of the annular chamber 2034 and/or other motion causes by the water within the annular chamber 2034.

Though the second aspect of the invention, e.g., the tube-in-tube heat exchanger 2020, is described in connection with the diverter 2070 of FIG. 30, it is noted that the tube-in-tube heat exchanger 2020 can utilize any diverter, including, but not limited to, the diverter 4234 of FIGS. 51-68 described below in connection with the third aspect of the present invention.

Referring to FIGS. 31-35, the upper tank portion 2036 shall now be discussed with further detail. The upper tank portion 2036 includes at least one inner wall portion 2122 extending about the axis A_(T) to define a portion of the external cavity 2026 extending along the axis A_(T). The upper tank portion 2036 further includes at least one outer wall portion 2124 extending about the axis A_(T), such that the inner wall portion 2122 and the outer wall portion 2124 define therebetween a portion of the annular chamber 2034 therebetween. Also, the upper tank portion 2036 has a top wall 2126 that is opposite the bottom wall 2088 of the lower tank portion 2038 and that extends from the inner wall portion 2122 of the upper tank portion 2036 to the outer wall portion 2124 of the upper tank portion 2036 to at least partially enclose the annular chamber 2034. As shown, each one of the inner and outer wall portions 2122, 2124 of the upper tank portion 2036 (and the inner and outer wall portions 2084, 2086 of the lower tank portion 2038) can have a cylindrical shape.

Referring to FIGS. 22 and 31-35, the upper tank portion 2036 is securingly aligned with the lower tank portion 2038. More particularly, the inner wall portion 2122 of the upper tank portion 2036 terminates at an end opposite the top wall 2126 of the upper tank portion 2036 with a first annular flange 2128. The first annular flange 2128 of the upper tank portion 2036 mates with the first annular finger set 2090 of the lower tank portion 2038, and the ribbon seal 2040 b is positioned between the first annular flange 2128 and the first annular finger set 2090. Also, the outer wall portion 2124 of the upper tank portion 2036 terminates at an end opposite the top wall 2126 of the upper tank portion 2036 with a second annular flange 2130. The second annular flange 2130 of the upper tank portion 2036 mates with the second annular finger set 2092 of the lower tank portion 2038, and the ribbon seal 2040 a is positioned between the second annular flange 2130 and the second annular finger set 2092. The upper tank portion 2036 is provided with an alignment tab 2132 that engages the alignment tab 2096 of the lower tank portion 2038 to secure the upper tank portion 2036 thereto.

The upper tank portion 2036 has formed therein a plurality of passages, including a water outlet passage 2134 and a refrigerant tube inlet 2136. Each of the water outlet passage 2134 and the refrigerant tube inlet 2136 extend from the outer wall portion 2124 of the upper tank portion 2036 and proximal the top wall 2126 thereof. The refrigerant tube inlet 2136 has external threads 2138 for engagement with the seal assembly 2072 a as further discussed below with reference to FIG. 44. The water outlet passage 2134 has an annular groove 2140 formed at an end thereof for receiving the ring seal 2060 a and is further discussed below in connection with the water outlet nipple 2022. The alignment tabs 2096, 2132 cooperate with one another to securingly align the upper and lower tank portions 2036, 2038, such that the water outlet passage 2134 of the upper tank portion 2036 extends parallel with respect to the water inlet passage 2100 of the lower tank portion 2038.

Referring to FIGS. 22, 32, and 34, the annular chamber 2034 includes an area proximal the water outlet passage 2134 that, for the purposes of those embodiments of second aspect of the present invention having the diverter 2070, is referenced herein as a water convergence area 2142. As best shown in FIG. 22, an “open area,” e.g., the water convergence area 2142, is provided where the refrigerant tube end 2054 a extends past the water hose end 2052 b. In the second aspect of the invention, water from the primary water passage 2058, as well as leakage flow rising through the annular chamber 2034 from the loose seal formed at the diverter 2070, converge at and/or proximal the water convergence area 2142 for flow out through the water outlet passage 2134.

In embodiments of the invention having a diverter, such as the substantially-enclosed diverter 4234 of FIGS. 51-68 described below, the “open area” discussed above enables the flow of water from the water hose end 2052 b of the primary water passage 2058 to fill those areas of annular chamber 2034 of the tank 2032 external of the tube-in-tube assembly 2046.

Referring to FIGS. 22 and 36-39, the water outlet nipple 2022 and the water inlet nipple 2024 shall now be discussed with further detail. As shown in FIGS. 22 and 36-37, the water outlet nipple 2022 includes a generally cylindrical wall 2144 a with a tank attachment end 2146 a and a line attachment end 2148 a opposite the tank attachment end 2146 a. The tank attachment end 2146 a includes an annular flange 2150 a that mates with the annular groove 2140 of the water outlet passage 2134 of the upper tank portion 2036. As shown in FIG. 22, the ring seal 2060 b is positioned between the annular groove 2140 and the annular flange 2150 a. The line attachment end 2148 a has an annular groove 2152 a formed therein and external threads 2154 a for coupling the water outlet nipple 2022 to that portion of the fluid circulation line (not shown) of the recreational body of water that is downstream of the tube-in-tube heat exchanger 2020. The line attachment end 2148 a can be provided with any additional and/or alternative structure suitable for coupling the water outlet nipple 2022 to the fluid circulation line.

Referring to FIGS. 22 and 38-39, the water inlet nipple 2024 is similar in some respect to the water outlet nipple 2022. For the example, the water outlet nipple 2024 includes a generally cylindrical wall 2144 b with a tank attachment end 2146 b and a line attachment end 2148 b opposite thereto. The tank attachment end 2146 b includes an annular flange 2150 b that mates with the annular groove 2106 of the water inlet passage 2100 of the lower tank portion 2038, and the ring seal 2060 a is positioned between the annular groove 2106 and the annular flange 2150 b. The line attachment end 2148 b has an annular groove 2152 b formed therein and external threads 2154 b for coupling the water inlet nipple 2024 to that portion of the fluid circulation line (not shown) of the recreational body of water that is upstream of the tube-in-tube heat exchanger 2020. The line attachment end 2148 b can be provided with any additional and/or alternative structure suitable for coupling the water inlet nipple 2024 to the fluid circulation line.

Continuing with reference to FIGS. 22, 38, and 39, the water inlet nipple 2024 can advantageously be provided with other features. For example, the exemplary water inlet nipple 2024 has a first passage 2156 formed therein for receiving the temperature sensor 2062, such that the first passage 2156 is in fluid communication with water flowing through the cylindrical wall 2144 b for sensing the temperature of such water. A plurality of annular bosses 2158 are formed on the outer surface of the cylindrical wall 2144 b for securingly aligning the mounting strap 2064 that is used to removably secure the temperature sensor 2062 to the water inlet nipple 2024. As another example, the exemplary water inlet nipple 2024 has a second passage 2160 formed therein for receiving the drain plug 2066, such that the second passage 2160 is in fluid communication with water flowing through the cylindrical wall 2144 b for drainage thereof. In this regard, a depression 2162 having a radius greater than that of the second passage 2160 is provided in alignment therewith for receiving the drain plug seal 2068.

Referring to FIGS. 22 and 40-44, the seal assemblies 2072 a, 2072 b shall now be discussed with further detail. As shown in FIGS. 22 and 40, the refrigerant tube 2050 includes the refrigerant tube ends 2054 a, 2054 b and a refrigerant tube body 2164 extending therebetween. The refrigerant tube body 2164 preferably has a spiraled outer surface for inducing turbulent flow of water in the primary water passage 2058, thereby facilitating more efficient heat transfer. However, the refrigerant tube ends 2054 a, 2054 b preferably have substantially cylindrical outer surfaces to be received by the seal assemblies 2072 a, 2072 b, respectively. Further discussion of the seal assemblies 2072 a, 2072 b (and the refrigerant tube ends 2054 a, 2054 b) shall now be made with respect to the seal assembly 2072 a (and the refrigerant tube end 2054 a), and it shall be understood that such discussion is similarly applicable with respect to the seal assembly 2072 b (and the refrigerant tube end 2054 b).

Referring to FIGS. 40-44, the seal assembly 2072 a includes the O-ring 2074, the piston 2076, the grommet 2078, the cap 2080, and the compression nut 2082. The seal assembly 2072 a further includes a continuous cylindrical opening 2166 extending through the O-ring 2074, the piston 2076, the grommet 2078, the cap 2080, and the compression nut 2082 along a central axis, referenced herein as axis A_(SA). The continuous cylindrical opening 2166 has a radius just greater than that of the refrigerant tube end 2054 a, such that the refrigerant tube end 2054 a extends through and out of the continuous opening 2166 (see FIG. 44). The seal assembly 2072 a is operable between a relaxed state and a compressed state, in which the cap 2080 cooperates with the piston 2076 to compress the grommet 2078 when the compression nut 2082 has engaged the external threads 2138 of the refrigerant tube inlet 2136.

The compression nut 2082 includes an open end 2168 and a cylindrical, internally-threaded wall 2170 for respectively receiving the refrigerant tube inlet 2136 into an internal chamber 2172 of the nut 2082 and mating with the external threads 2138 thereof. The compression nut 2082 further includes a flat annular wall 2174 opposite the open end 2168 extending radially inward from the internally-threaded wall 2170 of the compression nut 2082. An opening 2176 extends through the flat annular wall 2174 along the axis A_(SA). In some embodiments of the present invention, the O-ring 2074, the piston 2076, the grommet 2078, and the cap 2080 are each received into the internal chamber 2172 of the nut 2082.

The piston 2076 is positioned proximal the refrigerant tube inlet 2136 (or, in the case of the seal assembly 2072 b, the refrigerant tube outlet 2102) and is received by the compression nut 2082. The piston 2076 includes an annular piston wall 2178 that defines that portion of the continuous opening 2166 extending through the piston 2076 and further includes a tapered section 2180 that tapers in a direction toward the refrigerant tube inlet 2136 (or, in the case of the seal assembly 2072 b, the refrigerant tube outlet 2102). The annular piston wall 2178 has a first portion 2182 with a first inner radius that is just greater than that the refrigerant tube ends 2054 a, 2054 b and a second portion 2184 with a second inner radius that is greater than the first inner radius, such that the second portion 2184 is widened to receive the grommet 2078 for seating thereof at the tapered section 2180. An annular rim 2186 extends radially outward from the tapered section 2180 and terminates at a position adjacent the internally-threaded wall 2170.

The piston 2076 includes an annularly grooved flange 2188 that extends from the rim 2186 concentrically with respect to the first portion 2182 of the annular piston wall 2178. The annularly grooved flange 2188 receives in a groove 2190 thereof the O-ring 2074, such that the O-ring 2074 is spaced apart from the internally-threaded wall 2170 of the compression nut 2082. The grooved flange 2188 and the first portion 2182 of the annular piston wall 2178 define a first annular space 2192 therebetween, which is further discussed below.

The piston 2076 further includes a lipped flange 2194 having a flange 2196 that extends from the rim 2186 substantially concentrical with respect to the second portion 2184 of the annular piston wall 2178 and that, together with the second portion 2184 of the piston wall 2178, defines a second annular space 2198.

It is desirable for the walls of the piston 2076 to be of substantially equal thickness to minimize warping, including, for example, the flange 2196, the second portion 2184 of the piston wall 2178, the grooved flange 2188, and the first portion 2182 of the piston wall 2178. In this regard, the first and second annular spaces 2192, 2198 are sized and dimensioned for such purposes.

The flange 2196 terminates at an end opposite the rim 2186 with a piston lip 2200 that extends radially toward the internally-threaded wall 2170 of the compression nut 2082, such that the lipped flange 2194 and the annularly-grooved flange 2188 of the piston 2076 cooperate with the internally-threaded wall 2170 of the compression nut 2082 to define an annular space, herein referenced as a receiving area 2202, for receiving the external threads 2138 of the refrigerant tube inlet 2136 (or, in the case of the seal assembly 2072 b, the external threads 2104 of the refrigerant tube outlet 2102).

Continuing with reference to FIGS. 40-44, the grommet 2078 is formed of a resiliently deformable material, such as rubber. The grommet 2078 includes a substantially cylindrical grommet body 2204 defining therein a portion of the continuous opening 2166 having a radius just greater than each of the refrigerant tube ends 2054 a, 2054 b. The grommet 2078 further includes a beveled portion 2206 extending from the body 2204 and also defining therein a portion of the continuous opening 2166 having a radius just greater than each of the refrigerant tube ends 2054 a, 2054 b. The grommet 2078 is received by the piston 2076, such that the beveled portion 2206 of the grommet 2078 is positioned within a space (not designated) defined by the tapered section 2180 of the annular piston wall 2178, and such that the grommet body 2204 is positioned within a space (not designated) defined by the second portion 2184 of the annular piston wall 2178. In some embodiments of the invention, the grommet can include a second beveled portion (not shown) at an end of the grommet 2078 opposite the beveled portion 2206.

The cap 2080 is received by the piston 2076 and is positioned between the grommet 2078 and the compression nut 2082. The cap 2080 includes an annular wall, which is referenced herein as a cap body 2208, and which defines therein a portion of the continuous opening 2166 of the seal assembly 2072. The cap body 2208 is received within the second portion 2184 of the annular piston wall 2178 in abutment with the grommet 2078. The cap 2080 further includes a lip, which is referenced herein as a cap lip 2210, and which extends radially from the cap body 2208 at an end thereof opposite the grommet 2078 and proximal the flat annular wall 2174 of the compression nut 2082. The radius of the cap lip 2210 is greater than the radius of the opening 2176 that extends through the flat annular wall 2174, such that the cap lip 2210 abuts the flat annular wall 2174.

As indicated above, each one of the seal assemblies 2072 a, 2072 b has a relaxed state when disengaged from a corresponding one of the external threads 2104, 2138 and a compressed state when engaged with the corresponding one of the external threads 2104, 2138. In this regard, with continuing discussion of the seal assemblies 2072 a, 2072 b by way of exemplary reference to the seal assembly 2072 a, an embodiment of the seal assembly 2072 a having the relaxed state is shown in FIG. 43 and an embodiment of the seal assembly 2072 a having the compressed state is shown in FIG. 44.

Referring to FIG. 43, it is shown that when the seal assembly 2072 a is in the relaxed state (e.g., when it is disengaged from the external threads 2138), the grommet 2078 maintains its natural shape described above. Moreover, the cap 2080 is sized, shaped, and dimensioned, such that the cap lip 2210 defines an open channel 2212 with the piston lip 2200.

Referring to FIG. 44, it is shown that when the seal assembly 2072 a is in the compressed state, e.g., when it is engaged from the external threads 2138, the refrigerant tube end 2054 a extends through the continuous opening 2166 and the grommet 2078 is compressed to form a tight seal with the refrigerant tube end 2054 a, while the compression nut 2082 engages the external threads 2138. In having positioned the external threads 2138 within the receiving area 2202 to engage the internally-threaded wall 2170 of the compression nut 2082, the external threads 2138 force the piston lip 2200 to close the channel 2212 and into abutment with the cap 2210, such that the cap 2210 is secured between the piston lip 2200 and the flat annular wall 2174 of the compression nut 2082. The grommet 2078 is compressed between the piston 2076 and the cap 2080, thereby being deformed radially outward to form a seal with the refrigerant tube end 2054 a.

Further sealing is provided by the O-ring 2074, such that when the external threads 2138 are positioned within the receiving area 2202, the O-ring 2074 compresses forming a tight seal. Refrigerant can flow through the seal assemblies 2072 a, 2072 b, while the flow of water therethrough is inhibited.

Referring to FIGS. 22, 27 and 45-46, the legs 2042 a-c shall be discussed with further detail. Because leg 2042 a is similar to leg 2042 b, it shall be understood that the discussions and drawings of leg 2042 a are similarly applicable with respect to the leg 2042 b. Each one of the legs 2042 a-c is formed of a unitary structure that includes a base 2214, a fastening tab 2216, and a hole 2218 that extends through the fastening tab 2216 for receiving a corresponding one of the screws 2044 a-c. In this regard, the legs 2042 a-c can be secured to the base plate 2014 of heating unit 2010.

The base 2214 of the leg 2042 c has a first leg elevation E_(L1), and each base 2214 of the legs 2042 a, 2042 b has a second leg elevation E_(L2) that is greater than the first leg elevation E_(L1). In this regard, the legs 2042 a-c can support the tank 2032 despite the bottom wall 2088 of the lower tank portion 2038 being multiform. For example, each one of the legs 2042 a-b can be positioned along the bottom wall 2088 where the lower tank portion 2038 has a first distance H₁, while the leg 2042 c can be positioned along the bottom wall 2088 where the lower tank portion 2038 has a second distance H₂. In such example, that amount by which the second leg elevation E_(L2) is greater than the first leg elevation E_(L1) is substantially equal to that amount by which the second distance H₂ is greater than the first distance H₁ (e.g., E_(L2)−E_(L1)=H₂−H₁).

Referring to FIGS. 29 and 45-48, the leg 2042 c has a first shaped depression 2220 formed in an end of the corresponding base 2214 opposite the fastening tab 2216. Each one of the legs 2042 a-b has a second shaped depression 2222 formed in an end of the corresponding base 2214 opposite the fastening tab 2216. In this regard, the first shaped depression 2220 is adapted to securingly receive the shaped post 2098 c, and each one of the second shaped depressions 2222 is adapted to securingly receive the shaped posts 2098 a, 2098 b. More particularly, the male shape of the shaped post 2098 c is complementary to the female shape of first shaped depression 2220, and the male shape of the shaped posts 2098 a-b is complementary to the female shape of the second shaped depression 2222. The male shape of the shaped post 2098 c is different than the male shape of each of the shaped posts 2098 a-b, and the female shape of first shaped depression 2220 is different than the female shape of each of the second shaped depressions 2222. Such differences inhibit a user from inadvertently securing one of the legs 2042 a-c out of position during assembly of the tube-in-tube heat exchanger 2020.

Referring to FIGS. 20-23, an exemplary use of the tube-in-tube heat exchanger 2020 shall now be discussed with further detail. To secure the tube-in-tube heat exchanger 2020 to the heating unit 2010, for example, the tube-in-tube heat exchanger 2020 is secured to the base plate 2014 inside the cabinet 2012. The compressor 2028 is positioned within the external cavity 2026 of the tube-in-tube heat exchanger 2020 and may be secured to the base plate 2014. The tube-in-tube heat exchanger 2020 is provided in fluid communication with the compressor 2028 by securing the external tube extensions 2030 a, 2030 b to the refrigerant tube ends 2054 a, 2054 b, respectively, as well to the refrigerant inlet and outlet (not shown) of the compressor 2028. Additional components suitable for use in the heat cycle may be provided in communication with the extensions 2030 a, 2030 b.

The cover 2018 is secured to the cabinet 2012 opposite the base plate 2014. In this regard, the tube-in-tube heat exchanger 2020 and the cover 2018, both alone and in combination, reduce the amount of sound emanating from the compressor 2028 to a user thereof. For flow of water, the water inlet nipple 2024 and the water outlet nipple 2022 are respectively secured to the upstream and downstream sides of the fluid circulation line for the recreational body of water.

When activated, there is preferably a counter-flow as between the refrigerant and the water to enhance heat transfer. In this regard, the tube-in-tube heat exchanger 2020 receives refrigerant proximal the top wall 2126 of the tube-in-tube heat exchanger 2020, such that the refrigerant is received at the refrigerant tube inlet 2136, which travels into the refrigerant tube end 2054 a, through the refrigerant tube 2050 to the refrigerant tube end 2054 b, and out of the refrigerant tube outlet 2102 proximal the bottom wall 2088 of the annular tank 2032. Similarly, the tube-in-tube heat exchanger 2020 receives water proximal the bottom wall 2088 of the tube-in-tube heat exchanger 2020, such that the water is received at the water inlet passage 2100 via the water inlet nipple 2024, which travels into the diverter 2070 (or another suitable diverter, such as the diverter 4234 of FIGS. 51-68 described below). In the second aspect of the present invention having the diverter 2070, a primary water flow flows through the primary water passage 2058 to the convergence area 2142, a leakage flow flows up through the annular chamber 2034 to the convergence area 2142, and the water of the leakage flow and the water of the primary flow converge and flow out of the water outlet nipple 2022 via the water outlet passage 2134. In an embodiment of the second aspect of the present invention having the substantially-enclosed diverter 4234 of FIGS. 51-68 described below, a primary water flow flows through the primary water passage 2058 to the open area, where water can fill the annular chamber 2034 and flow our through the water outlet nipple 2022.

The tube-in-tube assembly 2046 enhances the efficient transfer of heat from refrigerant in the refrigerant tube 2050 to water flowing through the primary water passage 2058. Moreover, in the second aspect of the invention, by positioning the tube-in-tube assembly 2046 within an annular chamber 2034 that allows for an upward leakage flow of water (or by otherwise filling the annular chamber 2034), the transfer of heat is made further efficient, by having heat that might otherwise be lost to the atmosphere from the water hose 2048, transferred to the water in the annular chamber 2034 (including the leakage flow, for example) for convergence with the primary flow at the convergence area 2142.

Heat transfer is further enhanced by virtue of the chamber 2034 having an internal negative geometrical shape that is annular which minimizes the amount of water external the hose 2048 that is not in direct surface-to-surface contact with the hose 2048. Additional features may be included for enhancing heat transfer. For example, it is contemplated that the water hose 2048 can be corrugated and/or the refrigerant tube body 2164 can have a spiraled outer surface, either or both for inducing turbulent flow within the primary water passage 2058, thereby enhancing heat transfer.

Referring to FIGS. 49-50, it is contemplated that some embodiments of the invention might be provided with a tube-in-tube assembly 2046 having centering means for centering the refrigerant tube 2050 within the water hose 2048. In this regard, the water hose 2048 is shown to be transparent in FIGS. 49-50 to facilitate consideration and discussion of such centering means. The centering means is optional, and the tube-in-tube assembly 2046 is not defined so as to require inclusion of the centering means.

Such centering means can include, for example, a plurality of hanger sets 2224, each one of the hanger sets 2224 spaced from each other one of the hanger sets 2224 along the length of the tube-in-tube assembly 2046. Each one of the hanger sets 2224 includes a plurality of rigid, radially-spaced hangers, such as an opposing pair of hangers 2226 a, 2226 b. Each one of the hangers 2226 a, 2226 b includes a corresponding one of a plurality of hook portions 2228 a, 2228 b, a corresponding one of a plurality of arm portions 2230 a, 2230 b, and a corresponding one of a plurality of arcuate anchor portions 2232 a, 2232 b. The hook portions 2228 a, 2228 are secured to the refrigerant tube 50, and each one of the hook portions 2228 a, 2228 b is radially and evenly displaced from each other one of the hook portions 2228 a, 2228 b. Each one of the arm portions 2230 a, 2230 b extends from a corresponding one of the hook portions 2228 a, 2228 b to a corresponding one of the arcuate anchor portions 2232 a, 2232 b through a corresponding slit (not shown) formed in the water hose 2048. The curvature of the arcuate anchor portions 2232 a, 2232 b preferably follows the curvature of the water hose 2048, and the length of the arm portions 2230 a, 2230 b is selected such that the anchor portions 2232 a, 2232 b pull the refrigerant tube 2050 with equal force and within the primary water passage 2058, such that the refrigerant tube 2050 is centered within the water hose 2048. Water escaping through the slits from the primary water passage 2058 to that area external thereof in the annular chamber 2034 joins the upward leakage flow.

Additional and/or alternative centering means are contemplated. For example, it is contemplated that the ribs forming corrugations in the water hose 2048 and/or the spiraled outer surface of the refrigerant tube body 2164 can be sized and shaped so as to center the refrigerant tube 2050 within the water hose 2050, while still defining a primary water passage 2058 therebetween for flow of water.

With principal reference to FIGS. 51-68, the third aspect of the present invention shall now be discussed with further detail. In discussing the third aspect of the present invention, additional reference is made to FIGS. 1-16 and 20-50 and the descriptions above corresponding thereto.

Referring to FIG. 51, a heat system is shown to include an embodiment of a header 3010 in combination with an embodiment of a tube-in-tube heat exchanger 4020. Each of the header 3010 and the tube-in-tube heat exchanger 4020 shall be further discussed below, and elements of the header 3010 and the tube-in-tube heat exchanger shown in FIG. 51 which correspond substantially to the elements described above with reference to FIGS. 1-16 and 20-50 have been designated by corresponding reference numerals increased by two thousand. The third aspect of the invention shown in FIGS. 51-68 is constructed and used in manners consistent with the foregoing descriptions of the header 1010, the tube-in-tube heat exchanger 2020, etc. in connection with FIGS. 1-16 and 21-50 unless it is stated otherwise. Accordingly, it shall be understood that the heat system, including the header 3010 and/or tube-in-tube heat exchanger, can be provided with the features described above in connection with FIGS. 1-16 and 21-50.

Continuing with reference to FIG. 51, the tube-in-tube heat exchanger 4020 includes a diverter for inhibiting leakage therefrom, which is referenced herein as a substantially-enclosed diverter 4234 and which is shown in FIGS. 53-68, and the bypass function can be provided by the header 3010. Exemplary water flow to and from the tube-in-tube heat exchanger 4020 and/or the header 3010 has been designated as follows: water flow from a fluid circulation line (such as the fluid circulation line 1012 of FIG. 1) to an inflow side 3018 of the header 3010 has been designated as flow path FW_(IN1); water flow from the inflow side 3018 to a water inlet nipple 4024 of the tube-in-tube heat exchanger 4020 has been designated as flow path FW_(IN2); water flow from a water outlet nipple 4022 of the tube-in-tube heat exchanger 4020 to an outflow side 3020 of the header 3010 has been designated as flow path FW_(OUT1); and water flow from the outflow side 3020 to the fluid circulation line (such as the fluid circulation line 1012 of FIG. 1) has been designated as a flow path FW_(OUT2). The header 3010 facilitates bypass of the tube-in-tube heat exchanger 4020, e.g., under a high pressure condition, and an exemplary bypass flow has been designated in FIG. 51 as flow path FW_(B).

Referring to FIGS. 22, 51, and 51-68 the tube-in-tube heat exchanger 4020 is constructed similar to the tube-in-tube heat exchanger 2020, and the diverter 4234 can be utilized. The tube-in-tube heat exchanger 4020 includes the lower tank portion 2038, and the substantially enclosed diverter 4234 is positioned at a location that is referenced in the second aspect of the invention as the “diversion area” 2108 and that is proximal the water inlet nipple 4024. The water diverter 4234 is sized and shaped to direct principal water flow to the primary water passage 2058, and, in the third aspect of the present invention, the water diverter 4234 forms a friction fit against the tank 2032 and inhibits leakage flow of water from the diverter 4234 into the annular chamber 2034 outside of the primary water passage 2058.

Referring to FIGS. 22, 51, and 53-54, the substantially-enclosed diverter 4234 includes a first diverter portion 4236 and a second diverter portion 4238 that define a diverter chamber 4240 therein and that further define a gap 4242 through which the refrigerant tube end 2054 b extends. The first diverter portion 4236 and the second diverter potion 4238 define an interface means 4244 for joining the diverter 4234 to the tube-in-tube assembly 2046 for fluid communication therewith.

Referring to FIGS. 22, 51, and 53-61, the first diverter portion 4236 includes a first curved wall 4246 that has an inlet 4248 for receiving water from the header inflow side 3018 via the water inlet nipple 4024 and the water inlet passage 2100. The first diverter portion 4236 has a first inner surface 4250 and a first outer surface 4252 that is opposite the first inner surface 4250 and that forms a friction fit with the outer wall portion 2086 of the lower tank portion 2038 proximal the water inlet passage 2100. A first depression 4254 is formed in the first outer surface 4252 for the purposes described below.

The first curved wall 4246 defines a first body portion 4256 and a first tapered portion 4258 extending from the first body portion 4256. The first curved wall 4246 includes portions, which are referenced herein as first peripheral portions 4260, and which extend in a direction toward the second diverter portion 4238 and away from the outer wall portion 2086. The first peripheral portions 4260 partially enclose sides of the first tapered portion 4258 and the first body portion 4256, and define an opening, referenced herein as a first tapered opening 4262, and another opening, referenced herein as a first extension opening 4264. In this regard, the first tapered portion 4258, which tapers (gets smaller) in a direction away from the first body portion 4256, terminates at a first semi-annular end and at least partially circumscribes the first tapered opening 4262. A first semi-annular extension 4266 extends from the first peripheral portions 4260 so as to at least partially circumscribe the first extension opening 4264. For purposes that will be described further below, a flange 4269 extends from the first semi-annular extension 4266 and the first peripheral portions 4260 in a direction away from the outer wall portion 2086 and toward the second diverter portion 4238. Also for purposes that will be described further below, lips 4268 a, 4268 b are respectively provided on the first tapered portion 4258 and the first semi-annular extension 4266.

A plurality of hollow bosses 4270 extend from the first inner surface 4250 toward the second diverter portion 4238. As discussed with further detail below, the hollow bosses 4270 are configured to securingly receive a plurality of pins 4296 extending from the second diverter portion 4238 to align the first and second diverter portions 4236, 4238. A first plurality of ribs 4272 a-c extends from the first outer surface 4252 to enhance the friction fit with the outer wall portion 2086 of the lower tank portion 2038, thereby further inhibiting inadvertent movement of the diverter box 4234 relative to the lower tank portion 2038.

Referring to FIGS. 22, 51, 53-54, and 62-68, the second diverter portion 4238 includes a second curved wall 4274 and has a second inner surface 4276 and a second outer surface 4278 that is opposite the second inner surface 4276 and that forms a friction fit with the inner wall portion 2084 of the lower tank portion 2038 proximal the water inlet passage 2100. A second depression 4280 is formed in the second outer surface 4278. When the diverter 4234 is assembled, the second depression 4280 and the first depression 4254 cooperate to receive an O-ring, an elastomeric band, and/or another structure for securing together the diverter portions 4236, 4238.

The second curved wall 4274 defines a second body portion 4282 and a second tapered portion 4284 extending from the second body portion 4282. The second curved wall 4274 includes portions, which are referenced herein as second peripheral portions 4286, and which extend in a direction toward the first diverter portion 4236 and away from the inner wall portion 2084. The second peripheral portions 4286 partially enclose sides of the second tapered portion 4284 and the second body portion 4282, and define an opening, referenced herein as a second tapered opening 4288, and another opening, referenced herein as a second extension opening 4290. In this regard, the second tapered portion 4284, which tapers (gets smaller) in a direction away from the second body portion 4282, terminates at a second semi-annular end and at least partially circumscribes the second tapered opening 4288. The semi-annular ends of the first and second tapered portions 4258, 4284 form the gap 4242 through which the refrigerant tube end 2054 b passes. The radius of the gap 4242 is just greater than that of the refrigerant tube end 2054 b for sealing purposes. A second semi-annular extension 4292 extends from the second sidewall portion 4286 and at least partially circumscribes the second extension opening 4290. The first and second extensions 4266, 4292 form the interface means 4244, which has a radius just less than the water hose end 2052 a, and the interface means 4244 is inserted in the water hose end 2052 a to form a friction fit to facilitate secure fluid communication therebetween. Lips 4294 a, 4294 b are respectively provided on the second tapered portion 4284 and the second semi-annular extension 4292 in alignment with the lips 4268 a, 4268 b, respectively so as to form an annular shoulder on each end of the diverter 4234. O-rings, elastomeric bands, etc. (not shown) can be provided around each end of the diverter 4234 to secure the first diverter portion 4236 to the second diverter portion 4238, and the shoulders inhibit such O-rings from sliding off the diverter 4234.

To align the first and second diverter portions 4236, 4238 with one another, a plurality of pins 4296 extend from the second inner surface 4276, and each one of the pins 4296 is received within a corresponding one of hollow bosses 4270 aligned therewith. A second plurality of ribs 4298 a, 4298 b extend from the second outer surface 4278 to enhance the friction fit with the inner wall portion 2084 of the lower tank portion 2038, thereby further inhibiting inadvertent movement of the diverter box 4234 relative to the lower tank portion 2038. Similarly, a groove 4299 is defined within the second semi-annular extension 4292 that receives a portion of the flange 4269 formed in the first diverter portion 4238 for further aligning the first and second diverter portions 4236, 4238. Other portions of the flange 4269 can fit within the edge of the second plurality of sidewall portions 4286 for further alignment.

In use, the diverter 4234 directs the inflow of water from the inlet 4248 to the primary water passage 2058 formed between the water hose 2048 and the refrigerant tube 2050. The diverter 4234 inhibits leakage therefrom to the annular chamber 2034 of the tank 2032, thereby inhibiting flow from the diverter 4234 to a location that, with respect to the second aspect of the invention, is referenced above as the convergence area 2142. It is contemplated, though, that water will flow from such location to fill the annular chamber 2034 during operation of the tube-in-tube heat exchanger 4020.

With principal reference to FIGS. 51-52, the header 3010 shall now be discussed with further detail. As indicated above, the header 3010 is similar in construction to the header 1010 described above in connection with FIGS. 1-16. The header 3010 includes a manifold 3022, a service cartridge assembly 3028 therefor, and a connection means, such as a plurality of internally threaded lock rings 3204, 3206, for releasably securing the manifold 3022 to the water inlet nipple 4024 and the water outlet nipple 4022 at respective external threads 4154 b, 4154 a thereof.

The manifold 3022 and the service cartridge assembly 3028 therefor are similar in construction to the manifold 1022 and service cartridge assembly 1028 of FIG. 6, for example. The manifold 3022 can be formed of a plurality of segments, including an inflow unit 3208 at the inflow side 3018, an outflow unit 3210 at the outflow side 3020, and a cylindrical pipe 3212 forming the bypass port 3050 between the inflow unit 3208 and the outflow unit 3210. Each of the inflow unit 3208 and the outflow unit 3210 can have a hollow “T” configuration.

The inflow unit 3208 is provided with a first inflow chamber 3036, an annular bypass opening 3032, and a second inflow chamber 3044. The first inflow chamber 3036 can be provided with external threads 3214 (and/or otherwise configured) for attachment of the circulation line adapter assembly 1024 b, thereby securing the inflow unit 3208 of the manifold 3022 to the fluid circulation line 1012. The bypass opening 3032 can be provided with a radius just greater than that of the cylindrical pipe 3212, and mates with the cylindrical pipe 3212 by receiving same. Any fastening means can be used for securing the cylindrical pipe 3212 to the bypass opening 3032, such as glue, screws, etc.

The second inflow chamber 3044 can be provided with an annular shoulder, referenced herein as a first inflow shoulder 3216, and a first annular extension 3218 is provided with a radius just less than that of the second inflow chamber 3044. The first annular extension 3218 abuts the first inflow shoulder 3216 and is fastened to the inflow unit 3208 by glue and/or other suitable fastening means. A second inflow shoulder 3220 is provided at an end of the first annular extension 3218 that is opposite the first inflow shoulder 326 and proximal the water inlet nipple 4024 of the tube-in-tube heat exchanger 4020. The internally threaded lock ring 3204 engages the external threads 4154 b of the water inlet nipple 4024 to urge the second inflow shoulder 3220 against the water inlet nipple 4024, thereby securing the inflow unit 3208 and the header 3010 generally against and in fluid communication with the tube-in-tube heat exchanger 4020.

The outflow unit 3210 is provided with a first outflow chamber 3078, a bypass inlet 3222, second outflow chamber 3088, and a third outflow chamber 3148. The first outflow chamber 3078 can be provided with external threads 3224 for attachment of the circulation line adapter assembly 1024 a to secure the outflow unit 3210 of the manifold 3022 for flow from the outflow unit 3210 of the manifold 3022 to the fluid circulation line 1012. The bypass inlet 3222 can be provided with a radius just greater than that of the cylindrical pipe 3212 and mates with the cylindrical pipe 3212 by receiving same. Any fastening means can be used for securing the cylindrical pipe 3212 to the bypass inlet 3222, such as glue, screws, etc.

The second outflow chamber 3088 can be provided with an annular shoulder, referenced herein as a first outflow shoulder 3226, and a second annular extension 3228 is provided with a radius just less than that of the second outflow chamber 3088. The second annular extension 3228 abuts the first outflow shoulder 3226 and is fastened to the outflow unit 3210 by glue and/or other suitable fastening means. A second outflow shoulder 3230 is provided at an end of the second annular extension 3228 that is opposite the first outflow shoulder 2226 and proximal the water outlet nipple 4022 of the tube-in-tube heat exchanger 4020. The internally threaded lock ring 3206 engages the external threads 4154 a of the water outlet nipple 4022 to urge the second outflow shoulder 3230 against the water outlet nipple 4022, thereby securing the outflow unit 3210 and the header 3010 generally against and in fluid communication with the tube-in-tube heat exchanger 4020.

The third outflow chamber 3148 is configured to have pass therethrough flow from the second outflow chamber 3088 to the first outflow chamber 3078. The service cartridge assembly 3028 is inserted via a service opening (not designated) formed in the outflow unit 3210 opposite the bypass inlet 3222, and a lock ring 3150 is provided for securing the service cartridge assembly 3028 in place. Similar to the first aspect of the invention, when the flapper valve 3146 of the service cartridge assembly 3028 is in a closed position, the flappers obstruct fluid flow from passing through the bypass inlet 3222 to the third outflow chamber 3148 along the flow path FW_(B). However, when a high-pressure condition exists in the bypass pipe 3212 and/or there is a pressure-drop across the tube-in-tube heat exchanger 4020, the flappers open, at least partially, thereby permitting fluid flow from the bypass pipe 3212 to flow to the third outflow chamber 3148 along the flow path FW_(B).

It shall be understand that the features of the first and second aspects of the present invention can be included in the header 3010 and/or the tube-in-tube heat exchanger 4020 when suitable. For example, the header 3010 and the tube-in-tube heat exchanger 4020 can be provided with sensors for gauging temperature and/or pressure as described above, seal assemblies, and/or other features described above in connection with the first and second aspects of the invention.

It shall be further understood that the embodiments of the present invention described herein are merely exemplary and that a person skilled in the art may make many variations and modifications without departing from the spirit and scope of the invention. All such variations and modifications, including those discussed above, are intended to be included within the scope of the invention as defined in the appended claims. 

1. A heat system for allowing and inhibiting temperature alteration of water from a fluid circulation line in accordance with varying pressure, comprising: a heat exchanger having (i) a helical tube-in-tube assembly adapted for flow therethrough of water and a fluid for heat transfer therebetween, said tube-in-tube assembly having defined therein a primary water passage with a first end and a second end, and (ii) a tank with an annular chamber in which said helical tube-in-tube assembly is positioned; and a header having (i) an inflow side in fluid communication with said first end, (ii) an outflow side in fluid communication with said second end, (iii) a bypass configured for fluid communication with said inflow side and said outflow side, and (iv) a flapper valve, when oriented in a closed position, inhibiting fluid flow from said inflow side to said outflow side through said bypass, and, when oriented in an at least partially open position, permitting fluid flow from said inflow side to said outflow side through said bypass.
 2. The heat system of claim 1, wherein said tank defines an external cavity extending axially therethrough, and further including a compressor positioned within said external cavity, said compressor being in fluid communication with said helical tube-in-tube assembly for sending thereto and receiving therefrom said fluid.
 3. The heat system of claim 2, further including a base and a cover, said base and said cover cooperating with said at least one inner wall to at least partially enclose said compressor, thereby inhibiting the escape of sound from said external cavity.
 4. The heat system of claim 1, wherein said helical tube-in-tube assembly includes a water hose and a refrigerant tube at least partially extending through said water hose, said refrigerant tube and said water hose defining said primary water passage therebetween adapted for flow of water therethrough.
 5. The heat system of claim 4, further including a seal assembly releasably secured to said tank so as to permit refrigerant flow between said refrigerant tube and a tube external of said tank and so as to inhibit water flow out of said tank at said seal assembly.
 6. The heat system of claim 4, further including a substantially-enclosed diverter positioned within said annular chamber to direct a primary inflow of water into said primary water passage and inhibit leakage from said diverter into said annular chamber.
 7. The heat system of claim 6, wherein said substantially enclosed diverter is formed of a plurality of portions securingly aligned together to define a gap through which said refrigerant tube at least partially extends.
 8. The heat system of claim 1, further including a first leg having a first elevation and a second leg having a second elevation greater than said first elevation, said first leg and said second leg being releasably securable to said tank, wherein said tank includes a first post and a second post, said first leg including a first depression adapted to securingly receive said first post, said second leg including a second depression adapted to securingly receive said second post, wherein said second depression is shaped to inhibit insertion of said first post therein, and wherein said first depression is shaped to inhibit insertion of said second post therein.
 9. The heat system of claim 1, wherein said flapper valve includes a first flapper, a second flapper, and means applying a rotational force to said first and second flappers into said closed position of said flapper valve, each of said first and second flappers, when said flapper valve is in said closed position, being angularly displaced from another of said first and second flappers by a first angular amount, and each of said first and second flappers, when said flapper valve is in said at least partially open position; being angularly displaced from another of said first and second flappers by a second angular amount greater than said first angular amount.
 10. The heat system of claim 1, wherein said flapper valve is configured to be in said at least partially open position in response to a pressure drop across said heat exchanger.
 11. The heat system of claim 1, wherein said header includes a manifold at least partially defining said inflow side, said outflow side, and said bypass.
 12. The heat system of claim 10, wherein said manifold includes an inflow unit defining said inflow side, an outflow unit defining said outflow side, and a pipe defining said bypass.
 13. The heat system of claim 11, wherein each of said inflow unit and said outflow unit have a T configuration.
 14. A heat system for allowing and inhibiting temperature alteration of water from a fluid circulation line in accordance with varying pressure, comprising: a heat exchanger having (i) a helical tube-in-tube assembly adapted for flow therethrough of a plurality of fluids for heat transfer therebetween, and (ii) a tank defining an annular chamber in which said helical tube-in-tube assembly is positioned; and a header having (i) an inflow side in fluid communication with an inlet of said heat exchanger, (ii) an outflow side in fluid communication with an outlet of said heat exchanger; and (iii) a valve, when oriented in a closed position, inhibiting bypass flow from said inflow side to said outflow side, and, when oriented in an at least partially open position, permitting bypass flow from said inflow side to said outflow side.
 15. The heat system of claim 14, wherein said tank defines an external cavity extending axially therethrough, and further including a compressor positioned within said external cavity, said compressor being in fluid communication with said helical tube-in-tube assembly for sending thereto and receiving therefrom one of said plurality of fluids.
 16. The heat system of claim 15, further including a base and a cover, said base and said cover cooperating with at least one inner wall of said tank to at least partially enclose said compressor, thereby inhibiting the escape of sound from said external cavity.
 17. The heat system of claim 14, wherein said helical tube-in-tube assembly includes a water hose and a refrigerant tube at least partially extending through said water hose, said refrigerant tube and said water hose defining a primary water passage therebetween adapted for flow of water therethrough.
 18. The heat system of claim 17, further including a seal assembly releasably secured to said tank so as to permit refrigerant flow between said refrigerant tube and a tube external of said tank and so as to inhibit water flow out of said tank at said seal assembly.
 19. The heat system of claim 17, further including a substantially-enclosed diverter positioned within said annular chamber to direct a primary inflow of water into said primary water passage and inhibit leakage from said diverter into said annular chamber.
 20. The heat system of claim 14, wherein said valve is configured to be in said at least partially open position in response to a pressure drop across said heat exchanger.
 21. The heat system of claim 14, wherein said valve is a flapper valve configured to be in said at least partially open position in response to a pressure drop across said heat exchanger. 